
Class TJ^Q ^ 
Book_J±1_ 



COPYRIGHT DEPOSIT. 



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PRKPARbJj 

THE USE OP STUDENTS IN 'THh 

MECHANICAL ENGINEERING 

DEPARTMENT 

OP THE 



ASSACHUSETTS 

jOF TECHNOLOGY 

IRD P, MILLER 



1915 




NOTES 

ON 

POWER PLANT DESIGN 



PREPARED 

FOR THE USE OF STUDENTS IN THE 

MECHANICAL ENGINEERING 

DEPARTMENT 2^ 

OF THE SyK, 



MASSACHUSETTS 
INSTITUTE OF TECHNOLOGY 

EDWARD Fr MILLER 



1915 



Copyright, 1916 

BY 

EDWARD F. MILLER 



. H 7 



/ 



b 



U> 



',o 



■1^ 

aA420847 



FEB 21 1916 



INTRODUCTION 



An attempt has been made to assemble here, in condensed form, data which it is beUeved 
will be of assistance to one beginning on the laying out of a power plant. j 

Some of the material has been taken from articles which have appeared either in the Trans- 
actions of the American Society of Mechanical Engineers or in the engineering periodicals. 
Abstracts have also been made from Gebhardt's Steam Power Plant Engineering, from Koester's 
Steam Electric Power Plants, from Peabody and Miller's Steam Boilers, from Illustrations of 
Steam Engines, Steam Turbines, etc., from trade catalogues and from publications gotten out 
by manufacturers of the different pieces of apparatus which enter into the equipment of a power 
plant. 

E. F. M. 



TABLE OF CONTENTS 



Distribution of Heat 5, 6 

Boilers 7-15 

Methods of supporting; dimensions of; flues for; using fuel oil; stack for boilers using fuel oil. 

Economizers 16-23 

Calculation of size of; tables of dimensions of. 

Mechanical Stokers 24-25 

Chimneys, Flues and Draught 26-29 

Feed Pumps — Venturi Meter 29-33 

Engines 34-49 

Steam Consumption of; calculation of power of; cylinder efficiency of steam engines and steam 
turbines; Rankine efficiency and cylinder efficiency; calculation of bleeder type of engine 
or turbine; bleeding steam; comparison of engines and turbines and water rate of small tur- 
bines; general dimensions of and floor space required by engines. 

Condensers and Accessories 50-68 

Surface; jet; air pumps; dry air pumps; circulating pumps; exhaust relief valves. 

Flow of Steam in Pipes '. 69-71 

Feed Water Heaters 72-75 

Cooling Towers 76-80 

Calculation of; power required by fan; extra work put on circulating pump. 

Spray Nozzles . 80-81 

Centrifugal Pumps 82-90 

Characteristics of; friction of water in pipes. 

Coal Handling and Coal Bunkers 91-106 

Pivoted bucket conveyors; belt conveyors, scraper conveyor; power required; crushers; parabolic 
bins. 

Foundations, Concrete Floors, Walls 106-125 

Costs . 126-139 

Cost of various items entering into power house construction and into equipment of power 
house; cost of operation and distribution of operating costs; failure to make guarantees as 
to performance as affecting cost. 

Piping and Pipe Fittings 140-156 

Dimensions of fittings; list price and discounts; cast iron pipe for water work. 

Pipe Covering 157-159 

Cost of; insulating value of different thickness of; covering for flues and for boiler drums. 

Specifications 160-178 

Surface condenser; hot well pump; dry vacuum pump; low pressure turbine; direct acting boiler 
feed pump; automatic pump and receiver; horizontal cross compound non-condensing Cor- 
liss engine; steam driven centrifugal pumping unit; motor driven centrifugal pumping unit. 

Cuts of Stations 179-185 



DISTRIBUTION OF HEAT 



It is generally known that but a small proportion of the heat of the coal burned in a power 
plant goes into power. 

In cases where there is a large demand for steam for heating during eight months of the year 
the exhaust steam from the engines or turbines used for power or lights may be saved by 
utilizing this steam in the heating system. 

Under such conditions the cost of power for the period of heating is low and during this 
period the economy of the engine is of little moment provided there is never a surplus of exhaust 
steam. During the remaining four months when no heat is required, the economy of the engine 
is of importance. 

Under all conditions the efficiency of the boiler affects the cost of operation. 

The distribution of heat throughout a plant may be illustrated by the two cases worked 
out below. 

Case I 

Engine uses 30 lbs. steam, 100 lbs. gage per Brake Horse Power per hour; exhausting out- 
board. 

Feed water enters boiler at 70°. 

No heater installed. 

Per Cent hij Weight B. T. U. 

Engine 30 (1187-38) 100 34,470 

Feed Pump .6 (1187 -38) 2 689 

Drips, radiation .45 (1187 -38) 1.5 517 

35,676 
One horse power hour corresponds to 2,545 

2 545 
The thermal efficiency of the engine end = -^-x-^^r^ = .0713 

35,676 

The boiler supplying steam we will assume to use a coal of 14,600 B.T.U. to the lb. and that the 

Per Cent 

Per Cent of heat of coal utilized by boiler is ■......, 68 

Per Cent lost by radiation, loss of coal through grate, etc. is 10 

Per Cent of heat of coal carried off by flue gas is 22 

100 
14,600 X.68 = 9,928 B. T. U. 

Coal per Brake Horse Power Hour = -^ ' = 3.594 lbs. 

The overall efficiency of the plant is .0713 x.68 = .0485 

^^^^^^^^g 3.594 x\t 600 =-Q^^^ 

3.594 X 14,600 = 52,470 B. T. U. per I. H. P. hour. 



which may be found by dividing „ ^^. ' , , -^^ = .0485 

3.594 X 14,600 



NOTES ON POWER PLANT DESIGN 



Case IT 

Modern Turbine or Engine Plant using Superheated Steam at high pressure with 28" vacuum 
in condenser. Economizer, Primary and Secondary heaters installed. Coal 14,600 B. T. U. 
per lb. 

Combined Boiler and Economizer Efficiency = 76 per cent. 

Boiler pressure 184 lbs. absolute, superheat 52° F. Back pressure 1 lb. absolute. 

Feed water enters primary heater at 65°; leaves at 88°; enters secondary at 88°; leaves at 
150°; enters economizer at 150°; leaves at 300°. 

Engine or turbine requires 12.1 lbs. per I. H. P. hr. or 12.1 ^.93 = 13 lbs. per brake horse 
power hour. 

Per ( 

Engineor turbine 13 (1228.6 -118) 

Feed Pump 

Circulating Pump for Condenser 

Wet Pump . 

Dry Vacuum Pump 

Drips, radiation, etc. 



5 hy Weight 


B. T. U. 


100 


14,438 


1.5 


216 


3.0 


432 


1.5 


216 


1.5 


216 


1.5 


216 



15,734 



2,545 
15,734 



= .1617 the engine efficiency assuming feed pump part of engine room outfit. 



.1617 X.76 = overall efficiency = .1229 

The auxiliaries use 9% of engine steam, or .09 xl3 = 1.17 lbs. hr. per engine horse power. 
There is consequently 13 +1.17 = 14.17 lbs. passing through primary and secondary heater and 
through economizer per 13 lbs. supplied to engine. 

(88 - 65) 14.17 = 326 B. T. U. recovered in Primary heater. 

(150 - 88) 14.17 = 878 B. T. U. recovered in Secondary heater. 

The total coal per engine horse power output hr. is 



15,734 



= 1.418 lbs. 



524-70 B.T.U. from Coal -^ 



14,600 X.76 

1.418 X 14,600 = 20,702 B. T. U. supplied by coal per engine H. P. output. 

20,702 X.1229 = 2,545 B. T. U. put into work or one horse power hour. 

Had the primary and secondary heaters not been supplied there would have been required 

326 -1-878 
additional coal by an amount equal to .. . r.r.r, ^^ = -109 lbs. making the coal consumption per 

engine H. P. hr. = 1.528 lbs. 

The results of these two calculations have been plotted 
in Fig. 1, the area of the small square in each case repre- 
senting the heat units to be supplied for one horse power 
hour output. The full lines represent Case I and the 
dotted lines Case II. 

The heat exhausted outboard per horse power hour is for 
Case 1 35,676-2,545 = 33,131 B. T. U. 

The heat exhausted to the condenser in Case II is 
14,438 - 1,545 - 326 = 11,567 B. T. U. The 2,545 being 
the amount put into work and the 326 that transferred to 
the feed water in the primary heater. 

Many plants like that cited in Case I with constantly 
growing demands for power, have overloaded engines, and 
boilers which cannot be run at increased pressures. 

Often times if condensing water be available a low pres- 
sure turbine may be installed and the exhaust of the 
engine at from 1 to 5 lbs. gage pressure passed through the 



3S676 to Engine and Aux. -^ 


347 7 O to Engine -^ 
Z070Z B.TM. -from Coal^ 




15734- to Engine and Aux. \ 
~U'4S3~r^lEng//7e'-^~>\'^* 


254-5 





NOTES ON POWER PLANT DESIGN 7 

turbine and additional power amounting to from 50 to 80 per cent of the engine power obtained 
from the exhaust steam. 

In general an engine designed to run non-condensing is not made sufficiently strong and the 
bearing surfaces are not large enough to stand the extra load brought to the parts when the engine 
is run condensing. 



BOILERS 

With few exceptions every large power plant where the units are steam driven, is equipped 
with some form of water tube boiler. This type is selected (1) because large powers can be obtained 
from single units, (2) because of the saving in floor space over that of any other type suitable for 
large power houses and (3) because high steam pressures in large units can be carried without any 
appreciable thickening of the metal through which the heat of the fire is transmitted. 

A plant which is to be kept in continuous operation should have a sufficient number of units 
so that with one laid off for repairs the other units are able to carry the entire load. 

Hand fired boilers working with natural draft can be run 33 per cent above their rating, with- 
out difficulty, provided the draft at the smoke outlet at normal rating is at least .5" of water. 

Stoker fired boilers working either with forced draft, induced draft or with both forced and 
induced draft may be run at times of peak load at 300 per cent of their rating. In recent years 
the boilers in nearly all of the power stations have been planned to develop from 150 to 200 per 
cent of their rating during ordinary running, and even higher than the figures given in times of 
emergency. 

But little loss in thermal efficiency, results from forcing a boiler to 150 per cent of its rating. 

When boilers are supplied with attached superheaters it is not advisable to have any possibility 
of a large amount of saturated steam being drawn from the drums of the boiler as such a proce- 
dure would result in the burning out of the superheater. 

Boilers rated 400 to 600 H. P. cost per H. P., erected on foundations provided by the purchaser, 
from $16.50 to $17.50; with attached superheater, the price increases from $1.00 to $1.50 per H. P. 

If the demand on a boiler plant amounted to 3600 H. P. and 2000 H. P. were installed, the 
boilers running 180 per cent of their rating, the reduction in first cost would amount to ($16.50 + 
$1.50) xl600 = $28,800. Taking interest, taxes, insurance, repairs and depreciation as 13 per 
cent, the saving on overhead charge would amount to .13 x 28,800 = $3,744. Any slight loss 
in economy due to forcing the boilers would be more than offset by the reduced overhead on the 
building due to the smaller boiler room required. 

Water tube boilers are given a nominal rating on a basis of 10 sq. ft. of heating surface per 
boiler horse power. 

Tables giving some general dimensions of the Stirling, Heine and Babcock and Wilcox boilers 
follow. 

These may be useful in getting general overall dimensions, weights, etc. It is evident that 
any of these boilers may be modified within certain limits. 

As an illustration suppose it is found advisable to put in a B. & W. boiler 27 sections wide, 
14 tubes high, tubes 18 ft. long. What would be the increase in width and in height over a boiler 
21 wide and 9 high. 

The width increases approximately 7" per section and the height approximately 6" per tube, 
making the width and height of the boiler 19' - 6" and 18' — 3" respectively. 

With 4" tubes the heating surface added per tube is 

18' x4 X 3.1416 ^___ .^ 
r^ = 18.85 sq. ft. 

The 30 tubes add 566 sq. ft. or 57 H. P., making the rating 57 + 396 = 453 H. P. 

It must be remembered that adding heating surface does not necessarily increase the power 
of a boiler ; the grate surface must be increased in the proper proportion at the same time. Roughly 
a sq. ft. of grate is to be added for two 18 ft. tubes. 



8 NOTES ON POWER PLANT DESIGN 



HEINE WATER TUBE BOILER 

This boiler requires a space at the back as it is cleaned from the ends. Any number of boilers 
of this type can be set side by side. 

The space in front of the boiler should be sufficient to allow of the renewal of a tube. 

The length of setting from fire front to rear of brickwork is always 1 foot 4 inches longer than 
the length of the tubes, for instance, the setting of a 90 horse-power boiler is 17 feet 4 inches long 
and a 101 horse-power boiler is 19 feet 4 inches long. The shell with manhead extends about 15 
inches beyond rear of setting, so that if possible a 4-foot space should be allowed behind the setting 
for access to same. In special cases the manhole is placed in the front head, or an opening may 
be made in the building wall opposite manhole, in which case 2 feet behind setting will be sufficient. 
The width of setting may be determined by adding the thickness of brick walls to the width of 
furnace. Thus, three 101 horse-power boilers in a battery, with 19 inches side and 28 inches divi- 
sion walls, will be 19^' + 53" + 28" + 53" + 28" -f- 53" -t- 19" = 21' 1". Existing walls may be 
utilized where space is limited, and the outside walls here reduced to a furnace lining 9 or 10 inches 
thick. 

The grate-surface given for bituminous coal is such that the rating may be easily developed 
with a J/^-inch draught at the smoke outlet. The grate area given for anthracite pea coal is that 
necessary in order to develop the rating of the boiler with i'2-inch draught at the smoke outlet. 
For convenience of handling it is advisable to limit the grate length for anthracite coal to 7 feet 
6 inches. Where this does not give area enough for the desired maximum capacity it is necessary 
to increase the draught. Standard grate lengths are 6 feet 6 inches, 7 feet and 7 feet 6 inches. 

Safety-valves are provided as required to meet local inspection laws. 



NOTES ON POWER PLANT DESIGN 



Heine Water-Tube Boilers 







Tubes 31/2" 




Shells 






Steam Outlet 








Square 
Feet 


Diameter 
















Horse- 












Height of 


Diam. 


power 


Heating 
surface 












Height of 
Flange Above 


Center Line 
Above Floor 


Feed-pipe 






No. Length 


No. 


Diam 


Length 


Diam. 


Floor Level 


Level Speoia 1 










1 


Ins. 


Ft. Ins. 


Ins. 


Ft. Ins. 


Ft. Ins. 


Ins. 


90 


903 


53 16 


for 


36 


19 41/2 


4 


11 71/2 


9 91/2 


IV2 


101 


1010 


53 18 


all 


36 


21 41/2 


4 


11 71/2 


9 91/2 


IV2 


113 


1130 


68 16 


Horse 


36 


19 41/2 


4 


12 21/2 


10 41/2 


11/2 


126 


1263 


68 18 


Power 


36 


21 41/2 


4 


12 21/2 


10 41/2 


11/2 


127 


1273 


77 16 




36 


19 41/2 


5 


12 21/2 


10 41/2 


lly^ 


143 


1424 


77 - 18 




36 


21 41/2 


5 


12 21/2 


10 41/2 


11/2 


153 


1533 


94 16 




36 


19 4 1/2 


5 


12 91/2 


10 11 1/2 


11/2 


171 


1714 


94 18 




36 


21 41/2 


5 


12 91/2 


10 111/2 


11/2 


142 


1420 


86 16 




42 


19 6V2 


5 


12 8 1/2 


10 10 


11/2 


158 


1588 


86 18 




42 


21 61/2 


5 


12 8 1/2 


10 10 


11/2 


170 


1708 


105 16 




42 


19 6V2 


5 


13 31/2 


11 5 


11/2 


191 


1911 


105 18 




42 


21 61/2 


5 


13 31/2 


11 5 


11/2 


156 


1564 


95 16 




42 


19 6 1/2 


5 


12 8 1/2 


10 10 


11/2 


175 


1749 


95 18 




42 


21 61/2 


5 


12 8 1/2 


10 10 


IV2 


188 


1883 


116 16 




42 


19 6 1/2 


5 


13 31/2 


11 5 


11/2 


210 


2106 


116 18 




42 


21 6 1/2 


5 


13 31/2 


11 5 


11/2 


171 


1716 


104 16 




48 


19 91/4 


6 


13 21/2 


11 91/2 


2 


192 


1920 


104 18 




48 


21 91/4 


6 


13 21/2 


11 91/2 


2 


206 


2061 


127 16 




48 


19 91/4 


6 


14 21/2 


12 71/2 


2 


230 


2306 


127 18 


' 


48 


21 91/4 


6 


14 21/2 


12 71/2 


2 


224 


2244 


138 16 




- 48 


19 91/4 


6 


14 21/2 


12 71/2 


2 


250 


2508 


138 18 




48 


21 91/4 


6 


14 21/2 


12 71/2 


2 


262 


2621 


163 16 




48 


19 91/4 


6 


14 91/2 


13 21/2 


2 


293 


2931 


163 18 




48 


21 91/4 


6 


14 91/2 


13 21/2 


2 


241 


2417 


149 16 




48 


19 91/4 


6 


14 6 


12 10 


2 


270 


2702 


149 18 




48 


21 91/4 


6 


14 6 


12 10 


2 


282 


2826 


176 16 




48 


19 91/4 


6 


15 1 


13 5 


2 


316 


3160 


176 18 




48 


21 91/4 


6 


15 1 


13 5 


2 


258 


2586 


160 16 




48 


19 91/2 


8 


14 6 1/2 


12 101/2 


2 


289 


2892 


160 18 




48 


21 91/2 


8 


14 6 1/2 


12 10 1/2 


2 


302 


3024 


189 16 




48 


19 91/2 


8 


15 11/2 


13 51/2 


2 


338 


3383 


189 18 




48 


21 91/2 


8 


15 11/2 


13 51/2 


2 






Grates 






Space Occu 


pied 














Standard Setting 


Special Settng 


Low CeiUngs 


Blow off- 




Bituminous 




Anthracite 




Height 


Height 


Height 


Height 


Cocks, 




Coal 




Pea Coal 




over 


over 


over 


over 


IV2" 


Furnace 












Safety- 


Breeching 


Shell 


Breeching 


Diam. 


Width 


Length Area 


Length Area 




Valve 




at Front 




No. 


Ft. Ins. 


Ft. Ins. Sq. Ft. 


Ft. 


Ins. 


Sq. Ft. 




Ft. Ins. 


Ft. Ins. 


Ft. Ins. 


Ft. Ins. 


2 


4 5 


4 6 20.3 


4 


71/2 


20.4 




13 41/2 


12 8 


10 10 


11 2 


2 


4 5 


5 22.5 


5 


21/2 


23.0 












2 


4 5 


5 22 . 5 


5 


10 


25.7 




13 11 1/2 


13 4 


11 5 


11 11 


2 


4 5 


5 6 24.7 


6 


51/2 


28.6 












2 


5 


5 25.4 


5 


9 


28.8 




13 111/2 


13 4 


11 5 


11 11 


2 


5 


5 6 27.9 


6 


6 


32.5 












2 


5 


6 30.4 


6 


11 


34.7 




14 6V2 


13 11 


12 


12 7 


2 


5 


6 6 32.9 


7 


9 


38.8 












2 


5 7 


5 28.4 


5 


9 


32.2 




14 71/2 


13 9 


11 101/2 


12 6 


2 


5 7 


5 6 31.2 


6 


5 


35.9 












2 


5 7 


6 34.0 


6 


11 


38.6 




15 21/2 


14 4 


12 51/2 


13 2 


2 


5 7 


6 6 36.8 


7 


9 


43.4 












2 


6 2 


5 31.4 


5 


9 


35.4 




14 71/2 


13 9 


11 101/2 


12 7 


2 


6 2 


5 6 34.4 


6 


6 


39.9 












2 


6 2 


6 37.5 


6 


11 


42.7 




15 21/2 


14 4 


12 51/2 


13 2 


2 


6 2 


6 6 40.6 


7 


9 


47.7 












2 


6 9 


5 34.3 


5 


9 


38.8 




15 3 


14 7 


12 11 


13 9 


2 


6 9 


5 6 37.7 


6 


6 


43.6 












2 


6 9 


6 41.1 


6 


11 


46.8 




16 3'/2 


15 3 


13 9 


14 11 


2 


6 9 


6 6 44 . 5 


7 


9 


52.2 












2 


7 4 


5 44 . 6 


6 


11 


50.9 




16 31/2 


15 3 


13 9 


15 


2 


7 4 


5 6 48.4 


7 


9 


56.8 












2 


7 4 


6 6 48.4 


8 


1 


59.5 




16 101/2 


15 10 


14 4 


15 7 


2 


7 4 


6 52.0 


















3 


7 11 


6 6 48 . 2 


6 


11 


54.7 




17 41/2 


15 10 


14 


15 6 


3 


7 11 


6 52 . 2 


7 


9 


61.3 












3 


7 11 


6 6 52.2 


8 


1 


64.0 




17 IIV2 


16 6 


14 7 


16 2 


3 


7 11 


7 56.1 


















3 


8 6 


6 6 51.7 


6 


11 


58.6 




17 5 


15 10 


14 01/2 


15 6 


3 


8 6 


6 56. 0' 


7 


9 


65.6 












3 


8 6 


6 6 56.0 


8 


1 


68.6 




18 


16 6 


14 71/2 


16 2 


3 


8 6 


7 60.2 



















10 



NOTES ON POWER PLANT DESIGN 



Heine Water-Tube Boilers 











Tubes 
















Steam Outlet 










31/2" 






Shells 












Heiu-ht nt 








Square 


Diameter 
















Height of Center Line 




Horse 


- 


Feet. 
Heating 
















Flange Above P 
Floor 


ibove Floor 














Level 






surface 


No. Length 




No. 


Diam. Length 




Diam. 




Level 


Special 
















Ins. Ft. Ins. 




Ins. 




Ft. Ins. 


Ft. Ins. 


Double- 


280 




2808 


171 16 




2 


36 


19 41/2 




8 




14 1 


11 11 1/2 


shell 


314 




3140 


171 18 




for 


36 


21 41/2 




for 




14 1 


11 111/2 


boilera 


328 




3280 


202 16 




all 


36 


19 41/2 




all 




14 8 


12 6 1/2 




367 




3669 


202 18 




horse- 


36 


21 41/2 




horse- 




14 8 


12 6 1/2 




297 




2978 


182 16 




powers 36 


19 41/2 




powers 




14 \ 


11 ni/2 




333 




3330 


182 18 






36 


21 41/2 








14 1 


11 111/2 




348 




3479 


215 16 






36 


19 41/2 








14 8 


12 6 1/2 




389 




3892 


215 18 






36 


21 41/2 








14 8 


12 6I/2 




254 




2546 


154 16 






36 ■ 


19 41/2 








12 101/2 


10 101/2 






285 




2848 


154 18 






36 


21 41/2 








12 101/2 


10 lOi/a 


Two 


284 




2840 


172 16 






42 


19 6 1/2 








13 41/2 


11 4 


sections 


317 




3176 


172 18 






42 


21 6 1/2 








13 41/2 


11 4 


over 


341 




3416 


210 16 






42 


19 6 1/2 








13 111/2 


11 11 


one 


382 




3822 


210 18 






42 


21 6 1/2 








13 111/2 


11 11 


furnace. 


312 




3128 


190 16 






42 


19 6 1/2 








13 41/2 


11 4 




350 




3498 


190 18 






42 


21 6 1/2 








13 41/2 


11 4 




576 




3766 


232 16 






42 


19 6 1/2 








13 111/2 


11 11 




421 




4212 


232 18 






42 


21 6 1/2 








13 111/2 


11 11 




440 




4400 


274 16 






42 


19 6 1/2 








14 6 1/2 


12 6 




492 




4924 


274 18 






42 


21 6 1/2 








14 6 1/2 


12 6 




343 




3432 


208 16 






48 


19 91/4 








13 101/2 


11 9.V2 




384 




3840 


208 18 






• 48 


21 91/4 








13 101/2 


11 91/2 




412 




4122 


254 16 






48 


19 91/4 








14 101/2 


12 71/2 




461 




4612 


254 18 






48 


21 91/4 








14 101/2 


12 71/2 




482 




4822 


300 16 






48 


19 91/4 








15 51/2 


13 21/2 




539 




5396 


300 18 






48 


21 91/4 








15 51/2 


13 21/2 




448 




4488 


276 16 






48 


19 91/4* 








14 101/2 


12 71/2 




501 




5016 


276 18 






48 


21 91/4 








14 101/2 


12 71/2 




524 




5242 


326 16 






48 


19 91/4 . 








15 51/2 


13 21/2 




586 




5862 


326 18 






48 


21 91/4 








15 51/2 


13 21/2 




Blowoff 






Grates 


Space Occupied 


Diam. 












Standard Setting 


Special Setting, 


Low Ceilings 


Feed- 


Cocks, 


F 


urnace 




Bituminous 




Anthracite 


Height 


Hei 


ght 


Height 


Height 


pipe 


1 \L" 




Width 




Coal 




Pea Coal 


over 


over 


over 


over 


] 


Diam. 






L 


sngth Area 


Length 


Area 


Safety-Valve 


Breeching 


Shell 
at Front 


Breeching 


Ins. 


Nn 


Ft. 


Ins. 


F 


t. Ins. Sq. Ft. 


Ft. 


Ins. 


Sq. Ft. 


Ft. Ins. 


Ft. 


Ins. 


Ft. Ins. 


Ft. Ins. 


2 1/2 


"4" 


c 


1 


« 


55.2 


7 





63.6 


15 41/2 


15 


6 


13 1 


. 14 5 


21/2 

2y2 


for 


c 


1 


6 


6 59.8 


7 


10 


71.3 












all 


£ 


1 


e 


59.8 


8 


3 


74.5 


15 111/2 


16 


1 


13 8 


15 


2V2 
2V2 

2 1/2 


horse- 
powers 




1 
8 
8 


7 
e 

c 


6 64.4 
58.8 
6 63 . 6 


7 
7 



10 


67.5 
75.6 


15 41/2 


15 


6 


13 1 


14 6 






8 


e 


63.6 


8 


2 


79.0 


15- 111/2 


16 


1 


13 8 


15 1 


21/2 






) 8 




' 6 68.5 


















2-11/2 
2-1 1'i 




1( 


) 7 


r 


) 53 . 7 


5 


6 


57.7 


13 111/2 


13 


10 


11 11 


12 11 






) 7 




) 6 59.0 


6 


2 


64.8 












2-1 1/2 
2-11/2 
2-11/2 






L 9 




) 59 . 7 


5 


6 


64.5 


14 71/2 


14 


3 


12 41/2 


13 3 






I 9 
L 9 


c 


) 6 65 . 6 
) 71.5- 


6 
6 


2 

7 


72.0 
77.3 


15 21/2 


14 


10 


12 111/2 


13 10 


2-1 1/2 
2-11/2 
2-11/2 
2-11/2 
2-11/2 
2-1 1/2 






9 


e 


) 6 77.3 


7 


5 


86.7 




















> 65.7 


5 


6 


70.8 


14 71/2 


14 


3 


12 41/2 


13 9 








\ 


) 6 72 . 1 
) 78 . 6 


6 
6 


2 

7 


79.5 
85.4 


15 21/2 


14 


10 


12 111/2 


14 6 








i 


) 6 85 . 
) 85 . 


7 
7 


5 
9 


95.7 
100.0 


15 91/2 


15 


5 


13 6 1/2 


15 1 


2-2 










r 9 91.5 
5 71.5 


5 


7 


78.0 


15 3 


14 


7 


12 11 


13 9 


2-2 










> 6 78.5 


6 


2 


87.2 












2-2 








\ 


3 85 . 3 


6 


8 


93.6 


16 31/2 


15 


9 


13 9 


14 11 


2-2 








( 


3 6 92.8 


7 


5 


104.8 












2-2 










3 92.3 


7 


9 


109.5 


16 101/2 


16 


4 


14 4 


15 6 


2-2 
2-2 






5 3 


( 


f 6 99 . 7 
5 92.7 


6 


8 


101.8 


16 31/2 


15 


9 


13 9 


15 


2-2 
2-2 






5 3 
5 3 


( 
f 


3 6 100.3 
3 100 . 3 


7 
7 


6 
10 


114.0 
119.1 


16 101/2 


16 


4 


14 4 


15 7 


2-2 






5 3 




1 6 108.0 



















NOTES ON POWER PLANT DESIGN 



11 



STIRLING BOILERS 

These boilers clean from the side, and only two can be set together without a space between. 
If necessary the boiler may be set without a space at the back, but it is advisable to have at least 
3 feet back of the rear wall. 

These boilers are also built with attached superheaters. The superheater is placed at differ- 
ent parts of the setting, according to the number of degrees of superheating desired. 

The following table gives dimensions of this boiler for different boiler horse-powers. 

If the boiler is equipped with a superheater, deduct 10 per cent from the rated horse-power. 
If, however, the superheater is flooded the capacity of the boiler is increased approximately 7 per 
cent above the ratings given. 



Horse-Power of Stirling Boilers 



CLASS 







B-low 


P 


E 


B 


A 


Q 


F 


R 


K 


L 


N 


Width of 












Height 














Setting 




11' 11" 


15' 41/2" 


15' 3" 


15' 8" 


18' 9" 


18' 10" 


20' 7" 


20' 8" 


214.10" 


22' 4" 


24' 6" 


Single 


Battery* 










Depth 












ft. in. 


feet 


14' 0" 


18' 7" 


16' 3" 


- 14' 0" 


16' 0" 


18' 9" 


16' 9" 


18' 2" 


17' 7" 


18' 3" 


18' 10" 


5 6 


10 


50 






50 
















6 


11 


55 




'75 


60 
















6 6 


12 


65 




90 


70 
















7 


13 


75 


iis 


100 


80 


iis 


i45 


lib 


i45 


i.56 


165 


i75 


7 6 


14 


85 


130 


115 


90 


130 


165 


155 


160 


170 


185 


195 


8 


15 


95 


145 


125 


100 


145 


180 


175 


180 


185 


205 


220 


8 6 


16 


105 


160 


140 


110 


160 


200 


190 


200 


205 


230 


240 


9 


17 


115 


175 


150 


120 


175 


215 


205 


215 


225 


250 


260 


9 6 


18 


125 


190 


165 


130 


190 


235 


225 


235 


245 


270 


285 


10 


19 


135 


205 


175 


140 


205 


255 


240 


250 


260 


290 


305 


10 6 


20 


140 


220 


190 


150 


215 


270 


260 


270 


280 


310 


330 


11 


21 


150 


230 


200 


160 


230 


290 


275 


285 


300 


330 


350 


11 6 


22 


160 


245 


215 


170 


245 


310 


295 


305 


315 


350 


370 


12 -0 


23 


170 


260 


225 


180 


260 


325 


310 


325 


335 


370 


395 


12 6 


24 


180 


275 


240 


190 


275 


345 


330 


340 


355 


395 


415 


13 


25 


190 


290 


250 


200 


290 


360 


345 


360 


375 


415 


435 


13 6 


26 


200 


305 


265 


210 


305 


380 


360 


375 


390 


435 


460 


14 


27 


210 


320 


275 


220 


320 


400 


380 


395 


410 


455 


480 


14 6 


28 


220 


335 


290 


230 


335 


415 


395 


410 


430 


475 


505 


15 


29 


230 


350 


300 


240 


350 


435 


415 


430 


450 


495 


525 


15 6 


30 


240 


365 


315 


250 


360 


450 


430 


450 


465 


515 


545 


16 


31 


250 


375 


330 


260 


375 


470 


450 


465 


485 


540 


570 


16 6 


32 


260 


390 


340 


270 


390 


490 


465 


485 


505 


560 


590 


17 


33 


265 


405 


355 


280 


405 


505 


485 


505 


520 


580 


610 


17 6 


34 


275 


420 


365 


290 


420 


525 


500 


520 


540 


600 


635 


18 


35 


285 


435 


380 


300 


435 


545 


515 


540 


560 


620 


655 



sides. 



* The horse-power is double for battery width shown. Single boilers require an alley on one side; battery boilers require an alley on both 



12 



NOTES ON POWER PLANT DESIGN 



least 5 feet between each 



BABCOCK AND WILCOX BOILERS 

These boilers clean from the side. ,There must be a space of at 
set of two. 

The tables give space taken up by boilers with vertical headers. For inclined headers, any 
number of tubes high, add 3 feet 8 inches to the length given. A double-deck boiler is 10 inches 
higher than a single-deck boiler of same number of tubes high. 

Space must be left in front of the boiler to enable the lowest tube to be replaced. 







Babcock 


AND 


"Wilcox Veetical 


Header 


Boilers.— 


-s 


mg 


le Deck 












Hor.se- 










































power 


Heating 


Sections 










Drums 






















at 10 


surface, 






























Steam 






Square 


Square 
























Nozzle 






Opening 






Feet 


Feet 


Wide High Long N 


0. 


Dia. 




Length 






Dia. Flange 


Dia. 


Flange 














Ft. 






Ins. 




Ft. 


Ins. 




Ins. Ins 




Ins. 


Ins. 


One 




101.8 




1018 


6 


9 16 






36 




18 


7Vd 




5 11 






5 


11 


Boiler 




114.3 




L143 


6 


9 IS 






36 




20 


2 






5 11 






5 


11 


in 




117.5 




1175 


7 


9 


16 






36 




18 


7Vi 




5 11 






5 


11 


One 




132.0 




L320 


7 


9 18 






36 




20 


2 






5 11 






5 


11 


Battery. 


134.5 




1345 


8 


9 16 






42 




18 


71/4 




5 11 






5 


11 






151.0 




1510 


8 


9 18 






42 




20 


2 






5 11 






5 


11 






150.2 




L502 


9 


9 16 






42 




18 


71/4 




5 11 






5 


11 






168.7 




1687 


9 


9 18 






42 




20 


2 






6 121/2 




6 


121/2 






203 . 6 


2036 


12 


9 16 


< 




36 




18 


7V4 




8 15 






8 


15 






228.7 


2287 


12 


9 18 


2 




36 




20 


2 






5 11 






8 


15 






235 . 1 


2351 


14 


9 16 






36 




18 


7V4 




5 11 






8 


15 






264.0 


2640 


14 


9 18 


2 


36 




20 


2 






5 11 






8 


15 






269.0 


2690 


16 


9 16 


2 


42 




18 


7V4 




5 11 






8 


15 






302.1 


3021 


16 


9 18 


2 


42 




20 


2 






5 11 






8 


15 






300.5 


3005 


18 


9 16 


2 


42 




18 


71/4 




5 11 






8 


15 






337 . 5 


3375 


18 


9 18 


2 


42 




20 


2 






5 11 






8 


15 






352 . 7 


3527 


21 


9 16 


c 




36 




18 


71/4 




5 11 




10 


171/2 






396.0 


3960 


21 


9 18 


3 


36 




20 


2 






5 11 




10 


171/2 












1 


\Iud-drums 




Height from 






Front 


f 






3 rates 








Safety 
Valve 
















Floor to 
top of 






Boiler to 
Center of 










































Hand 


Blow-off 




Steam 






Steam 
















No 


DlQ 




I 


>ed 


Hole 


No. Dia. 




Outlet 






Outlet 




Length 




Width 




Area 




Ins 




I 


QS. 


No. 








Ft. Ins. 






Ft. 


Ins. 


Ft. 


Ins. 




Ft. Ins. 








3V 


'2 




11/2 


1 




2 




14 


8 






3 


2 




6 







3 10 




23.00 




3V 


'2 




11/2 


1 




2 




14 


8 








ar 




7 







3 10 




26.81 




31/ 


'2 




IV2 


1 




2V2 




14 


8 






8 


2 




6 







4 5 




26.50 




4 






11/2 


1 




21/2 




14 


8 












7 







4 5 




30.94 




4 






IV2 


2 




2 '72 




15 


2 












6 







5 




30.00 




4 






iy2 


2 




21/2 




15 


2 












7 







5 




35.00 




4 






iy2 


2 




IV2 




15 


2 












6 







5 7 




33.50 




4V 


'j 




11/2 


2 




2V2 




15 


2 












7 







5 7 




39.06 


2 


3V 






2 


3 


2 


2V2 




15 


8 












6 







7 4 




44.00 


2 


3V 


2 




2 


3 


2 


2'/2 




15 


8 












7 







7 4 




51.31 


2 


4 






2 


4 


2 


2V2 




15 


8 












6 







8 6 




51.00 


2 


4 






2 


4 


2 


2V2 




hi 


8 












7 







8 6 




59.50 


2 


4 






2 


4 


2 


21/2 




2 












6 







9 8 




58.00 


2 


4 






2 


4 


2 


2V2 




16 


2 












7 


• 




9 8 




67.66 


2 


4 






2 


4 


2 


21/2 




16 


2 












6 







10 10 




65.00 


2 


4V 


'2 




2 


4 


2 


2V2 




16 


41/2 












7 







10 10 




75.81 


3 


4 






21/2 


4 


3 


21/2 




15 


9 












6 







12 7 




75.50 


3 


4 






2V,. 


4 


3 


2V2 




15 


9 












7 







12 7 




88.06 




Spac 


e Occupiec 


1 


Ai 


5prox. 
eight 


Su 
1 


Lpprox. 
spended 
A' eight 




Approx. 

Total 
Weight 






Approx. 
































of 


Ir 


icluding 




of 






Shipping 












Length 


Widi 


.h 


Vi 


Taier 


\ 


Vater 




Setting 






Weight 


R 


ed Brick 




Fire-brick 


Ft. 


Ins. 


Ft. 


ins. 




























No. 




No. 


17 


91/2 


6 


8 


< 


),200 




29 


,300 




120 


,000 






26 ,000 






14 ,200 




3250 


19 


9 


6 


8 


1 


3,170 




31 


,300 




130 


,600 






27„500 






15,600 




3550 


17 


OVi 


7 


3 


1 


D,020 




32 


,100 




126 


,000 






28 ,600 






14 ,500 




3450 


19 


9 


7 


3 




1,080 




34 


,300 




137 


,800 






30 ,300 






16 ,000 




3700 


17 


91/2 


7 


10 




2 ,330 




38 


,600 




135 


,300 






32,700 






15,100 




3700 


19 


9 


7 


10 




i,720 




41 


,300 




147 


,000 






34 ,800 






16 ,600 




3950 


17 


91/2 


8 


5 




5,220 




41 


,300 




142 


,800 






36 ,400 






15 ,300 




3950 


19 


9 


8 


5 




1,670 




44 


200 




155 


100 






38 ,300 






16,700 




4100 


17 


91/2 


10 


2 


1! 


5,400 




59 


200 




151 


,500 






47 ,400 






15 ,800 




4000 


19 


9 


10 


2 


2( 


) ,.340 




63 


,200 




163 


,600 






50 ,300 






17 ,400 




4550 


17 


91/2 


11 


4 


2( 


),040 




64 


,900 




162 


,500 






53 ,600 






16 ,400 




4400 


19 


9 


11 


4 


2. 


2,160 




69 


,300 




175 


,100 






56 ,000 






17 ,900 




4700 


17 


91/2 


12 


6 


2- 


1,600 




78 


,000 




178 


,900 






62 ,200 






17,200 




4700 


19 


9 


12 


6 


2" 


7,440 




83 


,400 




191 


,900 






65 ,900 






18,900 




5200 


17 


91/2 


13 


8 


2( 


5,440 




83 


,600 




190 


,700 






68 ,400 






17 ,800 




4950 


19 


9 


13 


8 


2' 


) ,340 




89 


,300 




204 


,900 






72 ,500 






19 ,.500 




5300 


17 


9V2 


15 


5 


3( 


3,000 


1 


08 


,700 




209 


,800 






79,100 






18,100 




5200 


19 


9 


15 


5 


3. 


5,240 


1 


16 


,200 




224 


,100 






83 ,900 






20 ,000 




5400 



NOTES ON POWER PLANT DESIGN 



13 



Babcock and Wilcox Vertical Header Boilers, — Single Deck 





Horse-power 

at 10 

Sq. Feet 


Heating- 
surface 
Sq. Ft. 


Width of 

Settings 

Ft. Ins. 


Shipping 
Weight 


Red Brick 
Number 


Fire Brick 
Number 


Two 
Boilers 
in One 


203.6 
228.6 

235.0 
264.0 


2036 
2286 

2350 
2640 


11 11 
11 11 

13 1 
13 1 


52 ,000 
55 ,000 

57 ,200 
60 ,600 


20 ,300 
22 ,000 

20 ,900 
23,000 


6,500 
7,100 

6,900 
7,400 


Battery. 


269.0 
302.0 


2690 
3020 


14 3 
14 3 


65 ,400 
69 ,600 


21 ,900 
24 ,000 


7,400 
7,900 




300.4 
337.4 


3004 
3374 


15 5 
15 5 


72 ,800 
76 ,600 


22,200 ■ 
24 ,300 


7,700 
8,200 




407.2 
457.4 


4072 
4574 


19 6 
19 6 


94 ,800 
100 ,600 


26 ,800 
29 ,400 


8,000 
9,100 




470.2 
528.0 


4702 
5280 


21 10 
21 10 


107 ,200 
112 ,000 


27 ,900 
30 ,500 


8,800 
9,400 




538.0 
604.2 


5380 
6042 


24 2 
24 2 


124 ,400 
131 ,800 


30 ,200 
32 ,400 


9,400 
10,400 




601.0 
675.0 


6010 
6750 


26 6 
26 6 


136 ,800 
145 ,000 


. 31,600 
33 ,600 


9,900 
10 ,600 




705.4 
792.0 


7054 
7920 


30 
30 


158 ,200 
■ 167 ,800 


31 ,650 
34 ,750 


10 ,400 
10 ,800 



Both the B. & W. and the Stirhng have cleaning doors for blowing soot from the tubes on the 
side, consequently only two boilers can be placed side by side without an aisle. 

The height of the tubes above the grate can be made to suit the requirements of the engineer ; 
a much greater height is used now than was the custom a few years ago. 

In many boiler houses the boilers are located on the first floor above the basement which 
may be at ground level or below ground level. 

The space below the boiler is used for collecting the ash, for the main steam line and feed 
pump lines, for conveying machinery, etc. The boilers are supported, in such cases, by steel beams 
running between the columns which must be spaced to suit the width of the boilers used. 

The column spacing is often made unequal to allow for a 5 or 6 ft. aisle between batteries. 

In some cases where small units are installed, the two boilers in any one battery are carried 
at the front end by steel beams, running from the face of a column at one side of the battery to 
a similar column at the other side. This method of supporting requires a rather heavy beam. 
More often there is a column in the center of the battery. In every case the columns must be 
protected by a sleeve so that should the brickwork of the boiler become burned through, there 
would be no possibihty of the heat of the fire softening the column. 

This sleeve is frequently made of thin iron encircling the column to a height of three cr four 
feet above the tubes, the sleeve being open at the bottom and at the top to allow of a circulation 
of air between the sleeve and the column. 

When boilers are carried by beams attached to the side of the columns there is an eccentric 
load brought to the end columns. These columns adjacent to the aisles between batteries must 
be diagonally braced above the boilers on account of this eccentric loading. The back ends of 
the boilers may be supported in the same way as the front ends or I beam uprights resting on steel 
floor beams, may ssrve to carry the cross beams from which the drums of the boiler are suspended. 

When a boiler house is arranged with a double row of boilers, having a firing aisle in the centre 
the coal pocket is often suspended from the columns so as to utilize the space over the firing aisle. 

Economizers if used, would then be located over the boilers at the back end; this plan utilizes 
space otherwise wasted but makes a boiler room which is dark. An arrangement found in some 
of the large plants in Chicago secures both a well lighted and a well ventilated boiler room. 



14 



NOTES ON POWER PLANT DESIGN 



The boilers at both front and back are supported by columns which are carried up to the roof. 
A coai pocket is hung between these columns over each row of boilers and the middle bay, which 
is the firing aisle, is open to the roof, which in this bay is of the monitor type. 

FLUES FOR BOILERS 

The area of the flue leading from a row of boilers to the stack should be as great as the area 
of the stack designed to carry the row. It is evident that a greater draft obtained from a high 
stack would diminish the cross sectional area required by a shorter stack giving less draft. The 
old rule which applied to hand fired boilers by which the flue area was made from 1/8 to 1/10 the 
grate area does not hold with stoker fired boilers under which coal is burned at three times the 
rate found common with hand fired boilers. 

To illustrate the method of determining the size of the flue for a row of boilers let us assume 
that 5000 lbs. of coal are burned per hour under a battery of boilers. Chimney 150 feet high. 
Referring to the chart of chimney capacity in the section treating of chimneys, it is seen that a 
chimney 150 feet tall will take care of 176 lbs. of coal per hour per sq. ft. of chimney area accord- 
ing to Kent's values and 157 lbs. according to Christie's values. 

It appears from these figures that a flue of from 28 to 32 sq. ft. area is required. 



BOILERS USING FUEL OIL 

In the middle western states and in the southwestern part of the country oil is in general 
use for steam generation. 

On account of the sudden fluctuations in the price of oil here in the east very few concerns 
in this part of the country have used oil. 

Contracts are now being made, however, for delivery of oil at a fixed price through a long 
period of years and there is every reason to believe that the use of oil in this part of the country 
will increase. 

Texas oil has a heating value of approximately 18,500 B. T. U. per pound. It contains gen- 
erally about 2 per cent of moisture although in some cases as much as 25 per cent has been found. 

The gross efficiency of an oil fired boiler plant is with good management about 82 per cent; 
as 2 per cent of the steam made is used in heating the oil and in spraying it, a net efficiency of 80 
per cent may be expected. 

An efficiency of 75 per cent would be consid6red very good for a coal fired boiler, 70 being 
nearer that obtained in every day running in the best plants. 

The price of oil varies either side of $1.00 per barrel of 42 gallons, 8 lbs. to the gallon. 

A table giving the number of barrels of oil equivalent to a ton of coal burned with boiler effi- 
ciencies varying from 65 to 75 per cent will enable one to make a comparison of the cost of evapora- 
tion, using oil at so much a barrel as against coal of a certain price per ton. 

Heat Value of Coal 14,600 per lb. 



Equivalent Evaportation per lb. coal from and at 
212° F. in lbs 

Barrels of oil 336 lbs. to barrel 18,500 B. T. U. per 
lb. burned with 80 per cent net efficiency equiv- 
alent to one ton of coal of 14,600 B. T. U. to lb. 



Oil weighs 8 lbs. per gallon. 
42 gallons per barrel. 
The crude oil has to be stored in steel tanks, generally placed underground outside of the 
building. The oil in the tank must be heated by a steam coil in order to keep it sufficiently fluid 



Boiler Efficiency 


.750 


.725 


.70 


.675 


.650 


11.284 
5.543 


10.908 
4.257 


10.532 
4.110 


10.392 
3.964 


9.779 
3.817 



NOTES ON POWER PLANT DESIGN 15 

to flow through the suction pipe of the oil pump supplying the burners with oil under 30 to 50 lbs. 
pressure. The exhaust of the oil pump is frequently used to still further heat the oil before it enters 
the burner. 

The temperature of the oil should not be high enough to cause the gas to volatilize as this 
would cause the flame at the burner to be extinguished and might result in a flooding of the furnace 
and an explosion. 

The advantages and the disadvantages of petroleum as a fuel compared with coal are given 
in "Steam" thirty-fifth edition, Babcock and Wilcox Co.'s catalogue, page 214, as follows: 

The advantages of the use of oil fuel over coal may be summarized as follows: 

1st. The cost of handling is much lower, the oil being fed by simple mechanical means, result- 
ing in: 

2nd. A general labor saving throughout the plant in the elimination of stokers, coal passers, 
ash handlers, etc. 

3rd. For equal heat value, oil occupies very much less space than coal. This storage space 
may be at a distance from the boiler without detriment. 

4th. Higher efficiencies and capacities are obtainable with oil than with coal. The combus- 
tion is more perfect as the excess air is reduced to a minimum; the furnace temperature may be 
kept practically constant as the furnace doors need not be opened for cleaning or working fires; 
smoke may be eliminated with the consequent increased cleanliness of the heating surfaces. 

5th. The intensity of the fire can be almost instantaneously regulated to meet load fluctua- 
tions. 

6th. Oil when stored does not lose in calorific value as does coal, nor are there any difficulties 
arising from disintegration, such as may be found when coal is stored. 

7th. Cleanliness and freedom from dust and ashes in the boiler room with a consequent sav- 
ing in wear and tear on machinery; little or no damage to surrounding property due to such dust. 

The disdavantages of oil are : 

1st. The necessity that the oil have a reasonably high flash point to minimize the danger of 
explosions. 

2nd. City or Town ordinances may impose burdensome conditions relative to location and 
isolation of storage tanks, which in the case of a plant situated in a congested portion of the city, 
might make the use of this fuel prohibitive. 

3rd. Unless the boilers and furnaces are especially adapted for the use of this fuel, the boiler 
upkeep cost will be higher than if coal were used. This objection can be entirely obviated, how- 
ever, if the installation is entrusted to those who have had experience in the work, and the opera- 
tion of a properly designed plant is placed in the hands of intelligent labor. 

SIZE OF STACK REQUIRED FOR OIL BURNING BOILERS 

The cross sectional area of stack for an oil burning boiler need be only 60 per cent of that 
required by the same plant burning coal. This may be shown by a simple calculation. 

The composition of a semi-bituminous coal is approximately C = .85 11= .06 ash, sulphur 
moisture, etc. .09. 

Fuel oil is made up of C = .84, H = .12, S. N. O. and moisture .06. 

The air for coal = 11,5 x .85 + .06 x 34.5 = 12.34 lbs.; allowing 50 per cent dilution in order 
to get air to all parts of furnace gives 18.51 lbs. 

For oil 11.5 X .85 + .12 x 34.5 = 13.86; allowing 20 per cent for dilution gives 16.63 lbs. 

As the heat utilized by the boiler from a pound of coal is about 10,000 B. T. U., while that 
taken up from a pound of oil is about 14,800 B. T. U., it is evident that 1.48 lbs. of coal would be 
required to furnish the heat absorbed from one pound of oil and consequently the weight of gases 
from the coal fired boiler would in comparison with the oil be as 1.48 x 18.51 = 27.39 is to 16.63, 
which means that the same stack will with oil fired boilers have 1.65 the capacity of coal fired 
boilers. 

Many plants which are overloaded, which have insufficient chimney area and in which there 
is not room for the installation of mechanical stokers with forced or induced draft fans, have adopted 
oil burning. 



16 NOTES ON POWER PLANT DESIGN 



ECONOMIZERS 



Economizers are made up of cast iron tubes 4" to 4J^" inside diameter and 9' long. The tubes 
are turned at the end to a slight taper and are forced into top and bottom headers by hydraulic 
pressure. These headers are made to take different numbers of tubes, as is shown by the table 
of dimensions given on pages which follow. The lower headers project through the brick 
work housing and are joined together by a "bottom branch pipe" running lengthwise of the econo- 
mizer. This "bottom branch pipe" has on one side, a series of flanges for making the connection 
with the bottom headers and on the opposite side, in line with each header, a hand hole through 
which the header may be cleaned. The feed water enters this "bottom branch pipe" at the end 
of the economizer nearer the chimney and leaves the economizer at the top, at the end nearer 
the boiler. The top headers are similarly connected. This pipe joining the top headers is placed 
above, instead of at the end of the header, and at the opposite side of the economizer. In some 
cases means are provided for washing out the bottom headers, by sending a stream of water from 
a hose down through the tubes at the back end of the bottom headers and letting it flow along the 
entire length of the bottom headers and out through the clean-out openings directly opposite the 
headers. 

In setting up an economizer, room should be left opposite these clean-out openings so that a 
scraper can be put into each header to remove any scale which may lodge there, as the headers 
are sometimes cleaned out in this way instead of by washing out. 

In order to repair a tube and replace it by a second tube without dismantling that section or 
that header, a slot is made in the upper end of the tube with a chisel so as to enable the tube to 
be sprung together. The tube is then withdrawn from the bottom header in the following manner : 

A piece of iron shaped as shown by the accompanying sketch is pushed down inside the tube 
and moved to one side so as to engage the bottom end of the tube, this piece being held by a rod 
with thread and nut at the top. A second piece like a wedge, is held against the first piece by a 
second rod and prevents any side motion of the first piece. By screwing on the first nut the tube 
may now be withdrawn from the bottom header. The new tube is now inserted, driven into the 
bottom header, and a conical wedge used to make the joint between the tube and the top header. 
Sometimes a tube which has given trouble may be plugged and cut out of service. 

As the tubes are withdrawn through the top of the economizer, or in case of serious mishap, 
the entire section is taken up through the top of the economizer, — there should be sufficient room 
left over the economizer to allow for this. The arrangement of the brickwork should be such as 
to enable a section to be withdrawn without making it necessary to take down a large amount 
of masonry. 

The heating surface needed may be put either in one large economizer, through which all the 
gases from all of the boilers pass, or there may be a number of smaller economizers known as "unit 
economizers," one for each battery of boilers. With the first arrangement, any accident to the 
economizer which might put it out of service, would reduce the power of the boiler plant 10 or 
15 per cent. The draft would be reduced to a considerable amount by this arrangement. 

In the second arrangement, as only one unit would be cut out, in case of accident, the reduction 
in power of the boiler plant would be inappreciable. 

The flue gas leaving the boiler should have a direct passage to the chimney around the econo- 
mizer. Suitable dampers should be provided so that the gases may be sent either through the 
economizer or directly to the chimney. When the economizer is out of service both dampers at 
entrance and exit to the economizer should be closed. 

In general, an economizer will save from 8 to 15 per cent. In figuring whether the saving is 
going to pay for the interest on the first cost, and for the depreciation, the saving to be made in 
any particular case has to be taken into account. The life of an economizer is generally considered 
to be 20 years, and the cost set is generally taken as about $4.50 per boiler horse power or $10 to 
$12 per tube erected. This latter figure does not include an induced draft-outfit which if installed 
would add to the cost. 

Reducing the temperature of the flue gas by passing it through the economizer reduces the 
draft practically in the proportion that the absolute temperature of the flue gas is reduced. The 



NOTES ON POWER PLANT DESIGN 



17 




draft is still further reduced by the friction of the gas in passing through the economizer and in 
the many instances where the draft is poor, it would be unwise to install an economizer unless 
an induced draft fan were to be installed also. Usually on the side of the economizer there is a 
space about 12 inches wide left between the last tubes and the casing or brickwork, to allow of 
inspection. Sometimes there are two such passages, one either side of the economizer. These 
passages are closed by side dampers when the economizer is in use. 

Provision should be made for removing the soot from the bottom of the economizer. To 
remove the soot which collects on the tubes, scrapers are provided, these scrapers being in the 
form of loose collars which are alternately raised and lowered by chains operated from a shaft run- 
ning along the top of the economizer. If the economizer is only eight tubes wide, one shaft will 
serve, but if the economizer is ten or twelve tubes wide there should be two sets of shafts. In place 
of the brickwork walls a sectional covering of steel bolted together through angle irons may be 
used. This covering is insulated by building it up of two steel plates with 2" of magnesia or asbes- 
tos as an insulating material between. 

The economizers must each be provided with a relief valve of sufficient size, and with a blow- 
off valve. Various arrangements of economizers as appUed to different types of boilers, and the 
various arrangements of the direct flues may best be seen by studying some of the cuts of power 
stations or by referring to some of the cuts shown on later pages. 

The economizer is always connected on the feed line in such a way that the feed may be by- 
passed around the economizer, and when the economizer becomes steam bound it should be cut 
out and allowed to cool until the steam has condensed. 




The rise of temperature of the feed-water in an economizer may be calculated as follows: 
Th = temperature of flue gas entering economizer. 
Tc = temperature of flue gas leaving economizer. 
th = temperature of feed water leaving economizer. 



18 NOTES ON POWER PLANT DESIGN 

tc = temperature of feed water entering economizer. 
.24 = specific heat of flue gas. 

30 = number of pounds of water fed per boiler H. P. 
24 = pounds of flue gas per pound of coal. 

9 = probable evaporation of water per pound of coal. 

{Th - Tc) X 24 X y X .24 = 30 (th - ic) 

Tc= Th- 1.562 {ih - tc) 

For different evaporations or for different weights of flue gas per pound of coal the value to 
replace 1.562 may be easily figured. 

S = square feet of heating surface in the economizer per boiler H. P. or per 30 lbs. of feed 
water fed per hour. 

3 = B.T.U. transmitted per square foot of surface per hour per degree difference of tempera- 
ture between the gases outside the tubes and the water inside the tubes. As the coldest gas is 
at that end of the economizer at which the cold water enters and the hottest gas at the end where 
the water is hottest, there can be but little error in taking the difference of the mean tempera- 
tures of the gas and of the water. 

30 ih - Q = (^^^ - -^^) xSxS 



_ 20 tc + 2 S Th + .562 S h 
^~ . 20 + 2.562 S 

The Green Economizer Company use the following formula: 

S (Th -tc) 



th-tc = 



(5w +GC)S 
^ + 2GC 



In this w = pounds of feed water per boiler H. P. 

G = pounds of flue gas per pound of combustible. 
C = pounds of coal per boiler H. P. hour. 

This formula is practically the same as the one already worked out. 

Example 

Flue gas leaves the boiler and enters the econpmizer at 550°F. The feed water after passing 
through both a primary and a secondary heater enters the economizer at 200° F. What is the tem- 
perature of the feed water leaving the economizer? 

What is the temperature of the flue gases leaving the economizer? 

It is customary to provide from 3.5 to 5 sq. ft. of heating surface in an economizer per boiler 
H. P. Assume in this case 4 sq. ft. 

20 X 200 + 2 X 550 X 4 + .562 x 4 x 200 
'"' 20 + 2.562 X 4 

th = 292° 
Tc = 550 - 1.562 (292 - 200) = 407° 

The feed water is heated from 200° to 292° by the economizer. Suppose the boiler pressure car- 
ried in a battery of boilers to have been 164.8 lbs. ab. with 100° superheat, then theheat needed to 
make a pound of water at 200°' F. into superheated steam of pressure and conditions specified is 
1252 -168= 1084 B.T.U. 



NOTES ON POWER PLANT DESIGN 19 

92 
The economizer saved 92 B. T. U. per lb. of water or ^ = .0849 say 83^ per cent. On a 

coal consumption of 592 tons per week with coal at $4.20 per ton a saving of 83/^ per cent amoimts 
in the course of a year to 

.085 X 592 X 52 X $4.20 = $10,989 

The economizer consisting of 672 tubes cost at $12.00 a tube, $8,064; the piping etc. brought 
the cost up to $10,000. 

There should be charged against the economizer which may be assumed to be worn out in 
20 years, a certain percentage for depreciation (see later pages) which we will take as 3.02 per cent, 
interest 5 per cent, taxes 1.5 per cent, insurance 0.5 per cent and repairs 2.5 per cent making a 
total of 12.52 per cent. 

.1252 X $10,000 = $1,252 

The saving apparently amounts to 10,989 - 1,252 = $9,737 per year. 

If an induced draft had to be maintained there should be charged against the economizer the 
cost of running the fan and the interest, depreciation, etc. on the cost of the outfit. 

This would make the saving less. In spite of the fact that figures show a decided saving 
made by the use of an economizer many engineers will not recommend their installation. 

Some arrangements of economizers follow: 

The resistance offered to the flue gases by an economizer amounts to from .25" to 30" of water. 
In many instances on account of this loss of draft, it becomes necessary to install an induced draft 
fan. 

Illustrations of induced fan cutfits as erected in two manufacturing plants are shown. 



20 



NOTES ON POWER PLANT DESIGN 





GENERAL DIMENSIONS OF GREEN'S IMPROVED FUEL 

ECONOMIZERS 

Height over gearing, 13 ft. 514 in. Height over section, 10 ft. 2l^ in. 



in 


">. 






Dimensions Inside 


Area Between 






Xi 

3 


.0 

3 







Walls 


Tubes 


c ™ 


s 


h 


H ^ 


ai 


fc. 






It 

n c 


_ *^ 


"0 

J3 




"0 

Xi 


(^ 


3 »\ 


1 

j=3 E 


§ 2 
^11 


^•0 a 


u S. 
^=.■2 E 





= 5 


£ 


E 


B 


c 


- (fl ^ 




" ^ rt 


-•« i 


.-« n 


.;:<n S 


3 




3 
Z 


s 
Z 


3 

z 


nJ uj 


^ a 


%'"a 


g -Q 


& 


& 


& 


S. 


S 


32 


4 


8 


4'-10" 


3'-4" 


4'-l" 


4' 10" 


16.6 


23.85 


31.10 


1984 


408 


48 


4 


12 


T- 3" 


" 


" 


" 


" 


i ( 


< 1 


2976 


612 


64 


4 


16 


9'- 8" 


" 


" 


" 


" 


" 


" 


3968 


816 


80 


4 


20 


12'- V 


" 


i i 


i i 


t ( 


1 1 


ti 


4960 


1020 


96 


4 


24 


14'- 6" 


" 


" 


" 


" 


" 


" 


5952 


1224 


112 


4 


28 


16'-11" 


" 


" 


" 


" 


1 1 


" 


6944 


1428 


128 


4 


32 


19'- 4" 


" 


" 


" 


" 


" 


" 


7936 


1632 


144 


4 


36 


21'- 9" 


" 


' ' 


" 


" 


i i 


" 


8928 


1836 


160 


4 


40 


24'- 2" 


" 


" 


" 


" 


" 


" 


9920 


2040 


176 


4 


44 


26'- 7" 


" 


" 


" 


" 


i i 


i t 


10912 


2244 


192 


4 


48 


29' 0" 


' ' 


" 


" 


" 


" 


''' 


11904 


2448 


208 


4 


52 


31'- 5" 


" 


* * 


" 


' ' 


" 


" 


12896 


2652 


48 


6 


8 


4'-10" 


4'-8" 


5'- 5" 


6'- 2" 


21.85 


29.10 


36.35 


2976 


612 


72 


6 


12 


7'- 3" 


' ' 


" 


" 


* * / 


" 


" 


4464 


918 


96 


6 


16 


9'- 8" 


" 


" 


i i 


* * 


" 


" 


5952 


1224 


120 


6 


20 


12'- 1" 


' ' 


' ' 


• ' 


" 


" 


" 


7440 


1530 


144 


6 


24 


14'- 6" 


" 


' ' 


' * 


' ' 


" 


" 


8928 


1836 


168 


6 


28 


16'-11" 


' ' 


" 


' ' 


" 


i " 


" 


10416 


2142 


192 


6 


32 


19'- 4" 


' ' 


" 


" 


" 


" 


" 


11904 


2448 


216 


6 


36 


21'- 9" 


" 


' ' 


" 


" 


" 


" 


13392 


2754 


240 


6 


40 


24'- 2" 


' ' 


' ' 


' ' 


" 


" 


" 


14880 


3060 


264 


6 


44 


26'- 7" 


" 


" 


" 


" 


',' 


" 


16368 


3366 


288 


6 


48 


29'- 0" 


" 


* * 


* ' 


' ' 


" 


" 


17856 


3672 


312 


6 


52 


31'- 5" 


' ' 


" 


" 


I' 


" 


" 


19344 


3978 


336 


6 


56 


33'-10" 


" 


" 


" 


( i 


" 


" 


20832 


4284 


360 


6 


60 


36'- 3" 


' ' 


" 


" 


1 ( 


" 


" 


22320 


4590 


96 


8 


12 


7/. 3// 


6'-0" 


6'- 9" 


7'- 6" 


27.00 


34.25 


41.5 


5952 


1224 


128 


8 


16 


9'- 8" 


" 


" 


" 


" 


" 


" 


7936 


1632 


160 


8 


20 


12'- 1" 


' ' 


' ' 


" 


" 


" 


' ' 


9920 


2040 


192 


8 


24 


14'- 6" 


" 


" 


" 


ft 


" 


" 


11904 


2448 


224 


8 


28 


16'-11" 


" 


" 


i i 


' ' 


" 


" 


13888 


2856 


256 


8 


32 


19'- 4" 


" 


" 


" 


" 


" 


" 


15872 


3264 


288 


8 


36 


21'- 9" 


" 


i i 


" 


" 


• * 


■" 


17856 


3672 


320 


8 


40 


24'- 2" 


" 


" 


" 


" 


" 


" 


19840 


4080 


352 


8 


44 


26'- 7" 


" 


" 


" 


* ' 


" 


" 


21824 


4488 


384 


8 


48 


29'- 0" 


" 


' ' 


" 


" 


" 


" 


23808 


4896 


416 


8 


52 


31'- 5" 


" 


" 


" 


1 1 


" 


" 


25792 


5304 


448 


8 


56 


33'-10" 


" 


" 


" 


" 


" 


" 


27776 


5712 


480 


8 


60 


36'- 3" 


" 


" 


" 


" 


" 


" 


29760 


6120 


160 


10 


16 


9'- 8" 


7'-4" 


8'-l" 


8'-10" 


32.25 


39.50 


46.75 


9920 


2040 


200 


10 


20 


12'- 1" 


" 


" 


" 


" 


" 


'" 


12400 


2550 


240 


10 


24 


14'- 6" 


" 


" 


" 


" 


" 


" 


14880 


3060 


280 


10 


28 


16'-11" 


" 


" 


" 


i i 


" 


" 


17360 


3570 


320 


10 


32 


19'- 4" 


" 


" 


" 


" 


" 


" 


19840 


4080 


360 


10 


36 


21'- 9" 


( ( 


* ' 


" 


" 


( * 


" 


22320 


4590 


400 


10 


40 


24'- 2" 


7'-4" 


S'-l" 


8'-10" 


32.25 


39.50 


46.75 


24800 


5100 


440 


10 


44 


26'- 7" 


" 


" 


" 


•' 


'• 


" 


27780 


5610 


480 


10 


48 


29'- 0" 


" 


" 


" 


' ' 


" 


" 


29780 


6120 


520 


10 


52 


31'- 5" 


" 


" 


" 


" 


'< 


" 


32240 


6630 


560 


10 


56 


33' 10" 


" 


" 


" 


' ' 


" 


" 


34720 


7140 


600 


10 


60 


36'- 3" 


" 


" 


" 


" 


" 


" 


37200 


7650 


640 


10 


64 


38'- 8" 


" 


" 


" 


" 


" 


" 


39680 


8160 


680 


10 


68 


41'- 1" 


a 


i i 


" 


" 


' ' 


" 


42160 


8670 


720 


10 


72 


43'- 6" 


< ( 


" 


" 


" 


" 


" 


44640 


9180 


760 


10 


76 


45'-ll" 


" 


1 ( 


" 


" 


" 


" 


47120 


9690 


800 


10 


80 


48'- 4" 


" 


i i 


" 


" 


* ' 


* ' 


49600 


10200 


240 


12 


20 


12'- 1" 


8'-8" 


9'-6" 


10' 3" 


39.25 


44.75 


51.50 


14880 


3060 


288 


12 


24 


14'- 6" 


" 


" 


" 


" 


" 


" 


17856 


3672 


336 


12 


28 


16'-11" 


" 


" 


" 


" 


" 


" 


20832 


4284 


384 


12 


32 


19'- 4" 


" 


" 


" 


" 


" 


" 


23808 


4896 


432 


12 


36 


21'- 9" 


" 


" 


" 


" 


" 


" 


26784 


5508 


480 


12 


40 


24'- 2" 


" 


' ' 


" 


" 


" 


" 


29760 


■6120 


528 


12 


44 


26'- 7" 


( ( 


" 


" 


" 


" 


" 


32736 


6732 


576 


12 


48 


29'- 0" 


" 


" 


" 


" 


" 


1 1 


35712 


7344 


624 


12 


52 


31'- 5" 


" 


t ( 


" 


" 


tt 


'< 


38688 


7956 


672 


12 


56 


33'-10" 


1 ( 


" 


«' 


" 


" 


" 


41664 


8568 


720 


12 


60 


36'- 3" 


( < 


" 


" 


" 


" 


" 


44640 


9180 


768 


12 


64 


38'- 8" 


" 


" 


" 


" 


" 


" 


47616 


9792 


816 


12 


68 


41'- 1" 


"^ 


1 < 


1 1 


1 1 


t i 


" 


S0S92 


10404 


864 


12 


72 


43'- 6" 


4 ( 


II 


1 1 


1 1 


* * 


* * 


53568 


11016 



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24 NOTES ON POWER PLANT DESIGN 



MECHANICAL STOKERS 



There is no question about the desirability of mechanical stokers in a plant of 1500 H. P. 

While there may not be any saving in the cost of labor on a plant of 1500 H. P. the protec- 
tion against labor troubles which a stoker affords warrants its use on a plant of this size. 

On plants of larger size the saving in labor, together with the increased capacity to be obtained 
from the boilers, the freedom from smoke troubles, the insurance against labor troubles and the 
ability to push a boiler from a banked condition to 150 per cent rating in ten minutes make stokers 
absolutely necessary. 

The stokers may be divided into classes: 

(1) The Taylor and The Riley underfed stokers, both similar to the cut following. 

(2) The Murphy and the Roney, inclined grates. 

(3) The chain grate, like Green, Keystone, and the Babcock & Wilcox. 

(4) The American; The Jones; both underfed stokers but differing from the Riley and the 
Taylor. 

There are others not mentioned, the ones named being those most commonly found. 

The Taylor and the Riley are both capable of quick forcing and can be crowded harder than 
the Murphy or the Roney. All four of these are best suited for a good grade of soft coal. The 
chain grate works best on a poorer grade of coal. 

The American and The Jones are better suited for small units than for large units. 

Stokers cost from $6 to $10 per rated H. P. of the boiler. The higher figure includes the cost 
of the fan and engine required by certain types of stoker. 

See Steam Boilers, Peabody and Miller for more detailed discussion of stokers. 

The life of a stoker is from 6 to 8 years, consequently a high rate for depreciation must be 
charged against it. 



NOTES ON POWER PLANT DESIGN 



25 




DujTi ping Lever 



Tuyeres 




Speed 
Shaft 



Coal Hopper 



Dump Flate Guide 




26 



NOTES ON POWER PLANT DESIGN 



CHIMNEYS, FLUES AND DRAUGHTS 

The draft of a chimney depends upon the temperature of the gases entering the chimney, 
the temperature of the gases leaving the chimney, the height of the chimney and the temperature 
of the outside air. 

In figuring the draft, an average temperature of the outside air may be taken as 55°. 

As the draught of a chimney is due to the difference in weight of a column of cold air of the 
height of the chimney and the column of hot gas in the chimney, in order to figure the draft it is 
necessary to know the mean temperature inside the chimney. 

From work done on three or four chinmeys from 3' dia. 100 ft. tall to 16' dia. 250 ft. tall, the 
variation in temperature throughout the height of a stack has been plotted and an equation of 
the form i?T" = K fitted to the curve. 

H = height in feet of chimney at any point above middle of 

flue, the lower value of H being 3 ft. 
T = absolute temperature in degrees F. 
Ti = absolute temperature of gases entering chimney. 
iV =25 log K = 75.4032 

The mean absolute temperature is equal to 

area crosshatched 



HTt« 




i72-3 



This equals 




H.-2, 



Example: Assume temp, at a level 3 ft. above centre of 
flue as 1000° ab. Top of chimney 231 ft. above centre of flue. 
Find mean temperature and probable draft when outside air 
is at 55° F. 



1000x75 /231 



24 



24 
25 



231 -3 



873.0 



11.78 X 14.7 V (14.7 - .6 x .04) 



491.5 



873 



20.96 



— = .0477 

V 



12.39 X 14.7 V x 14.7 



491.5 



459.5 + 55 



12.97 — = .0771 



(.0771 - .0477) (231 
62.4 



■ 3) X 12 



= 1.29 



In the preceding calculation, the pressure in the chimney was needed, this was assumed to 
be (14.7 - .6 X .04) or the draft was assumed to be 1.20" at the bottom of the chimney. 

11.78 is the specific volume of flue gas. 
12.39 the specific volume of air. 



NOTES ON POWER PLANT DESIGN 



27 



The draught at the boiler will be less than that at the chimney end of the uptake on account 
of friction in the uptake, bends, etc. Generally .10" loss of draught is allowed for each 100 ft. of 
flue and .05" for each right angle bend. In addition to this there is from .25 to .3" lost due to 
resistance offered by the tubes of the boiler. In addition to this there is the resistance offered 
by the fuel bed and the grates. 




6 10 15 20 25 30 35 40 45 GO 

POUNDS OF COAL BURNED PER SQUARE FOOT OF ORATE SURFACE PER HOUR. 
CURVES SHOWING DRAFT REQUIRED BETWEEN FURNACE AND ASH-PIT AT DIFFERENT COMBUSTION RATES FOR VARIOUS KINDS OF COAL 



The amount of draft needed, or the loss of draft between the furnace and the ash pit, for dif- 
ferent kinds of coal burned at different rates has been determined by the Stirling Boiler Company 
from actual tests. 

The accompanying plot taken from their work needs no explanation. 

Example required draft needed at base of stack by a boiler 200 feet from chimney with 2 sharp 
bends in flue, the boiler burning run of mine bituminous coal at a rate of 25 lbs. of coal per square 
foot of grate per hour. 



Loss of draft between furnace and ash pit (plot) = .13" 

200 ft. flue loss = .20" 

2 sharp bends loss = ,10" 

Loss due to tubes and passages in boiler . = .30" 

.73" 



28 NOTES ON POWER PLANT DESIGN 

Example: A boiler plant has a chain grate burning 30 pounds of bituminous slack coal per 
square foot of grate per hour, a unit economizer and about 100 feet of flue. What should be the 
draft produced by the chimney? 

Boiler resistance 25 

Economizer resistance 30 

100 ft. flue '.'.'.'. !lO 

2 right angle bends jq 

Resistance through grate 44 

Draft required 1,19 



270 










































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250 


































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'-'' 


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^ 




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^ 


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y 
• 


^ 


^ 


y 


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y 




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150 


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130 


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90 



110 



.130 



150 



170 



190 210 

Height of Chimney 



230 



250 



270 



290 



With Taylor or Riley underfed stokers the air is delivered through the fuel bed under pressures 
of 4" to 6" of water, whatever may be needed to maintain a balanced draft over the fire; the stack 
is by this means relieved of the resistance offered by the fuel bed and generally gives sufficient 
draft to pull through an economizer. 

The gases after leaving an economizer are cooled and the draft of the chimney reduced because 
of the lower temperature. 

It will be found that adding 25 feet to the height of a chimney does not increase the draft very 
much. 

The dimensions of a chimney may be found with as great accuracy as is required by means 
of a chart which has been constructed from the tables of H. P. of chimneys given by Kent and 



NOTES ON POWER PLANT DESIGN 29 

by Christie (See Steam Boilers, Peabody & Miller). On this chart the capacities in lbs. of coal 
per hour per square foot of chimney area are given for different heights of chimney. Knowing 
the coal to be burned per hour, the cross sectional area for any assumed height may be calculated. 

The ratio of height to cross section must be considered, otherwise a poorly proportioned chim- 
ney may be obtained. 

For discussion of the stability of a chimney see Steam Boilers. In general the maximum com- 
pression due to both dead load and wind pressure is not allowed to exceed 10 tons per square foot. 



FEED PUMPS FOR BOILERS 

STEAM CONSUMPTION OF PUMPS 

The steam consumption of a duplex pump varies with the speed at which the pump runs. 

At half speed or at one-half rated capacity 125 to 150 pounds of steam will in general be re- 
quired per horse power hour of water work done. 

For slower speeds the rate may become as large as 200 or 250 lbs. At full speed and at rated 
capacity 90 to 100 pounds is a fair value to use for the steam consumption per water horse power 
per hour. 

Turbine driven centrifugals are now quite generally used as feed pumps in the larger power 
plants. 

The efficiency of a centrifugal pump designed for a given head and given capacity may reach 
80 per cent, but under the conditions which apply to centrifugals used as feed pumps a value between 
40 and 55 per cent should be used. The steam consumption for the driving end may be obtained 
from the curves already given. 



Drawings and table of dimensions of the Terry steam turbine with 
centrifugal feed pump are given on page 39. 



30 



NOTES ON POWER PLANT DESIGN 



THE KNOWLES HORIZONTAL DOUBLE ACTING PLUNGER PUMP. 

POT VALVE TYPE. 



End packed for 300 lbs. working water pressure. 
Center packed for 200 lbs. working water pressure. 



Center Packed 



4J 


2f 


6 


.11 


150 


16.5 


i 


1 


n 


1 


68x10 


4J 


23 


6 


.15 


150 


22.5 


i 


1 


n 


1 


68x10 


5J 


H 


7 


.25 


125 


31. 


i 


1 


2 


n 


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G 


m 


7 


.33 


125 


41. 


1 


L 


2 


n 


72x12 


6i 


4J 


8 


.46 


125 


57.5 


? 


li 


2% 


2 


75x12 


n 


4i 


10 


.69 


100 


69. 


1 


u 


2* 


2 


89x14 


8 


5 


10 


.85 


100 


85. 


1 


u 


3 


2h 


89x14 


8 


5 


12 


1.02 


100 


102. 


1 


n 


3 


2\ 


96x14 


10 


6 


12 


1.47 


100 


147. 


n 


U' 


3^ 


3 


98x22 


12 


7 


12 


2.00 


100 


200. 


2 


2h 


5 


4 


100 X 27 


14 


8 


12 


2.61 


100 


261. 


2 


2* 


5 


4 


102 X 27 


16 


9 


18 


4.96 


67 


332. 


2h 


3 


8 


6 


136 X 30 



End Packed 




■a 

o -3 


£ 

E -g 

r 


si 


PI 


Capacity per 
Minute at Maxi- 
mum Speed 


a. 

a S 


g a 
1" 


t 

a A 


1" 


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OS 


a " 
u 


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Oal3. 


4 


24 


5 


.11 


150 


16?s 


* 


1 


u 


1 


57x10 


5i 


3J 


7 


.25 


125 


31 


I 


1 


2 


14 


72x12 


6 


31 


7 


.33 


125 


41 


I 


1 


2 


14 


72x12 


7i 


31 


10 


.47 


100 


47 




li 


2 


14 


92x12 


n. 


4* 


10 


.69 


100 


69 




u 


2i 


2 


92x12 


8 


5 


10 


.85 


100 


85 




u 


3 


24 


92x12 


8 


4 


12 


.65 


100 


65 




u 


2i 


2 


112x12 


8 


5 


12 


1.02 


100 


102 




u 


3 


24 


112x12 


10 


5 


12 


1.02 


100 


102 


U 


n 


3 


24 


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10 


6 


12 


1.47 


100 


147 


U 


n. 


34 


3 


112x22 


12 


6 


12 


1.47 


100 


147 


2 


2h. 


34 


3 


114x22 


12 


7 


12 


2.00 


100 


200 


2 


2* 


5 


4 


120 x 27 


14 


7 


12 


2.00 


100 


200 


2 


2h 


5 


4 


120 X 27 


14 


8 


12 


2.61 


100 


261 


2 


2h 


6 


5 


124 X 27 


16 


8 


12 


2.61 


100 


261 


2\ 


3 


5 


4 


124x28 


16 


8 


18 


3.91 


67 


261 


2\ 


3 


6 


5 


164 X 30 


16 


9 


18 


4.96 


67 


332 


2\ 


3 


8 


6 


164x30 


18 


9 


18 


4.96 


67 


332 


2i 


3 


8 


6 


172 X 30 




In an emergency the capacities of these pumps can be doubled. For continuous work such 
as boiler feeding, speeds and capacities one half of those given are recommended. 



NOTES ON POWER PLANT DESIGN 



31 



THE VENTURI METER 

Nearly every large power plant has a Venturi meter in the boiler feed pipe. This meter may 
have a recording indicator or simply a Venturi meter manometer. The table following gives the 
sizes of the meters for boiler feed pipes as made by the Builders Iron Foundry of Providence, R. I. 

The Venturi meter manometer contains a well filled with mercury into whichaglasstubedips. 
The higher pressure from the inlet of the Venturi is conducted to the top of the mercury surface, 
and the lower pressure from the throat of the meter to the interior of the glass tube. The difference 
in these two pressures is indicated by the height of the single column of mercury within the glass 
tube. The rate of flow for any difference of pressures can be read opposite the surface of the mer- 
cury of the inner tube from the graduated scale shown at the left. The total quantity of water 
flowing may be obtained by taking readings periodically, averaging the same and multiplying the 
average by the elapsed time. The manometer is not suitable for installations where the rate of 
flow changes rapidly. For such cases the recording indicator shown would be preferable. 




Extra heavy meter tubes with "Manufacturers Standard" flange ends are usually selected 
for hot water. These are adapted to pre sures'up to 250 pounds per square inch. 



Inches 
D-iameter 
of Pipe 


Catalog 
Number 


Length 

of 

Meter Tube 


Boiler Horse Power 

30 lbs. per H. P. pel hour 


Pounds per Hour 


Gallons per Minute 


Mininiuni 


Maximum 


Mlomum 


Maximum 


Mlmmum 


Manmum 


2 


2^8 

21 


r-ii^s" 

I'-lOX" 
l'-7" 


45 

65 
115 


590 
850 
1500 


1360 
1960 
3470 


17600 
25400 
45100 




35 
50 
90 


T^ 


2J^A 
2KB 
2KC 


2'.45/8" 

2'-3" 

1'.113^" 


85 
115 
180 


1150 
1500 
2350 


2660 
3470 
5420 


34500 
45100 
70400 


11 


70 

90 

140 


3 


31 

31^ 


2'-ll" 

2'-73^" 
2'-4>^" 


115 
180 
260 


1500 
2350 
3380 


3470 
5420 
7820 


45100 

70400 

102000 


11 

16 


90 
140 
205 


4 


41^ 
41 H 
42 


4'-33/" 

3'-10%'' 

3'-6" 


180 
305 
465 


2350 
4000 
6000 


5420 
9170 
13900 


70400 
119000 
181000 


11 

18 
28 


140 
240 
360 


5 


515/8 

52 

52'/ 


5'- 13^" 

4'-8'/i" 
4'-2" 


305 
465 
725 


4000 
6000 
9400 


9170 
13900 
21700 


119000 
181000 
282000 


18 
28 
45 


240 
360 
560 


6 


62 
63 


5'-ll" 

5'-4// 

4'-IO" 


465 

725 

1040 


6000 
9400 
13600 


13900 
21700 
31300 


181000 
282000 
406000 


28 
43 
63 


360 
560 
810 

680 
950 
1440 


8 


82K 
83 K 
84 


7'-6K" 

6'-ll3,," 

6'-2" 


870 
1230 
1850 


11300 
16000 
24100 


26500 
36600 
55600 


344000 
476000 
722000 


53 

73 

111 


10 


103 -i 

104 

105 


9'-434'' 
7'-6" 


1230 
1850 
2900 


16000 
24100 
37600 


36600 
55600 
86900 


476000 

722000 

1129000 


73 
ill 

174 


950 
1440 
2260 


12 


124 
125 
126 


11 '-0" 
9'-ll" 
8'- 10" 


1830 
2900 
4200 


24100 
37600 
54200 


55600 
86900 
125000 


722000 
1129000 
1626000 


111 
174 

250 


1440 
2260 
3250 



32 



NOTES ON POWER PLANT DESIGN 




Glass 
Tube 



Graduated 
Scale 



Float 




O 



CHART RECORDER 

DIAL 

(Continuoash' records the 

rate of flow) 



INDICATOR DIAL 
(Shows the present rate of 
flow) 



DI:MENSI0NS, Etc. 
Base — 16 inches square 
Height — 6H feet 
Shipping Weight — 500 lbs. 



NOTES ON POWER PLANT DESIGN 33 

CALIBRATION TESTS ON METERS IN SERVICE 

Test No. 1. Made at Worcester Polytechnic Institute on 4-inch meter tube No. 2319, 1^ 
inch throat, equipped with manometer. Water was pumped through the meter tube into a verj' 
large wooden tank resting on platform scales, which form a part of the regular laboratory equip- 
ment. The manometer was placed on the floor immediately below the meter tube to which 
it was connected by flexible pipes. The rated capacity of this meter is 9,170 to 119,000 pounds 
per hoiu". The results were as follows: 



Numbers 


Pounds of Water Per Hour 


Error of Meter 


of Tests 


Meter Manometer 


Actual W'^eight 


Manometer 


1 


120,600 


122,640 


- 1.87% 


2 


90,000 


89,820 


+ 0.20% 


3 


59,950 


59,940 


+ 0.02% 


4 and 5 


30,000 


29,370 


+ 2.10% 


6 and 7 


9,000 


8,950 


+ 0.55% 



Test No. 2. Four-inch Venturi Meter (134-inch throat) at the plant of the Woonsocket 
(Mass.) Electric Machine & Power Company. Wtter pumped by duplex feed pump to two bar- 
rels which were filled alternately, the weight of water which each would hold having been deter- 
mined previously. The test lasted five hours and the flow was continuous. 

Corrected weight of water by barrels ..... 132,802 lbs. 
Corrected weight of water by Venturi . . . . . 131,000 lbs. 

Difference, 1.35%. 

Test No. 3. Four-inch Venturi Meter (134-inch throat) at plant of Brown & Sharpe Mfg. 
Company, Providence. Meter Tube was located on suction side of single plunger pump and 
course of water was from two calibrated open heaters (emptied alternately) to Meter Tube to pump. 

Total pounds of water by heaters ...... 392,453 lbs. 

Total pounds of water by Venturi Meter .... 397,104 lbs. 

Difference, 1.18%. 

Duration of test, 10 hours. 

A paper prepared by Prof. C. M. Allen presented before the A. S. M. E. gives a full discus- 
sion of the Ventiu-i Meter as applied for measuring feed water. 



34 NOTES ON POWER PLANT DESIGN 

ENGINES 

STEAM CONSUMPTION OF ENGINES 

The steam consumption of a simple non-condensing engine varies both with the cut-off and 
^^ ith the boiler pressure. 

There is but little gain in raising the pressure on a simple engine above 150 lbs. 

The variation in steam consumption per I. H. P. hour with the cut-off may be figured with 
reasonable accuracy from the full load consumption by multiplying the full load consumption 
by the following ratios: 



Load 


^ 


3^ 


M 


Full 


IVa 


Ratio 


1.26 


1.13 


1.09 


1 


1.05 



From tests on engines, of about the same type and size as the engine under consideration, 
working through the same ranges of pressure and temperature, from the same initial conditions, 
one can predict the probable performance with reasonable accuracy. 

In the absence of such tests the cylinder efficiency of a single valve non-condensing engine 
working with steam under 150 lbs. absolute may be taken between 55 and 65 per cent, when work- 
ing at its economical load. The cylinder efficiency of a four valve condensing engine may be taken 
at most economical load as from 66 to 72 per cent. The size of the engine, the valve gear, etc. 
all have an influence on the so-called "cylinder efficiency." 

This cylinder efficiency multiplied by the Rankine efficiency and by the mechanical efficiency 
gives the overall efficiency from which the steam consumption may be calculated as explained later 

CALCULATION OF POWER OF ENGINES 

The mechanical efficiency of an engine or the ratio of the brake power to the indicated horse 
power is between 90 and 93 per cent. 

The power of an engine at any speed and cut off may be found by drawing an indicator card 
using hyperbolae for expansion and compression lines, getting the M. E. P. from the card and 
then proceeding in the usual way. 

For a compound or triple expansion engine the M. E. P. is calculated on the assumption that 
the entire pressure drop is to be obtained in the low pressure cylinder. 
The ratio of cylinder volumes is 

for compound engines H. to L. 1 to 23/^ or 3 

in some rare cases 1 to 7 or 8 

for triple expansion engines H. to I. 1 to 3 

I. to L. 1 to 3M or 33/^ 
or H. to L. 1 to 93| or lOj/^. 

A calculation for Horse Power, which will give results more or less in error depending upon 
the accuracy with which one knows the multiplier used in getting the actual M. E. P. from the 
calculated, may be made as follows: — 

Calculated M. E. P. x multiplier x J^ X .7854 x 2 x Revs, x S 
^ •" 33000 

D = dia. low pressure cylinder in inches 
Revs. = revolutions per minute 

Pi = absolute initial pressure on a square inch 
P2 = back pressure absolute on a square inch 

N = No. of expansions = 77- — ^ 

^ H^xcutoff 

Cut-off is expressed as a decimal. 



NOTES ON POWER PLANT DESIGN 35 

S = stroke in feet 
H = dia. high in inches 

Calculated M. E. P. = -^+-^2.3026 %io N - Pi 

CYLINDER EFFICIENCY OF STEAM ENGINES AND STEAM TURBINES 

The ratio corresponding to the cylinder efficiency is for condensing turbine units about the same 
{%. e., .60 to .72) as for condensing steam engines; for non-condensing turbine units, however, the 
ratio is much lower than for non-condensing engines, the value being .40 to .49 as against .55 to .65. 

The higher the back pressure the lower the ratio becomes and .40 would apply for pressures 
of 50 to 70 lbs. absolute back pressure, .45 for back pressures about 35 lbs. absolute, and .49 for 
back pressures of 15 to 20 lbs. absolute. 

From these figures it is at once evident that the non-condensing turbine working against back 
pressure cannot compete in economy with the better class of non-condensing reciprocating engines. 

It is the custom in many manufacturing establishments to bleed steam from some stage of 
a turbine or from a receiver between the cylinders of a multiple expansion engine and to use this 
steam for industrial purposes. This is done rather than to draw live steam from the boilers through 
a reducing valve. 

It is also customary where there is a surplus of exhaust steam coming from the auxiliaries 
or in other words more steam than can be condensed in heating the feed water in a secondary heater, 
to exhaust this surplus into one of the low pressure stages of the turbine or into the second receiver 
of a triple engine and to thus get additional work out of this waste steam. 

Where steam is bled in this way a valve has to be provided to prevent steam from getting back 
into the turbine through the bleeder opening and causing the turbine to run away when under 
light load, at which time, boiler steam taken through a reducing valve would be fed into the bleeder 
Jine to supply at reduced pressure the steam needed for industrial purposes. 



RANKINE EFFICIENCY AND CYLINDER EFFICIENCY 

A simple calculation for a bleeder turbine with steam withdrawn at one of the higher stages 
and having the exhaust steam from the auxiliaries sent back into the low stage will serve to illus- 
trate the method of getting the steam consumption. 
Assume : 

2000 K. W. output at switchboard. 

Mechanical Efficiency of Turbine, 92%. 

Generator Efficiency, 93%. 

9000 lbs. steam bled out per hr. at 36 lbs. abs. 

2000 lbs. exhaust steam per hr. with 1.7% moisture put back at 15 lbs absolute. 

What is the steam consumption per K. W. hour with boiler pressure 177.5 lbs. ab. 97.3. Sup. 
and 1 lb. absolute pressure in condenser? 

Making use of a temperature entropy plot or diagram, the values maj'' be tabulated as below. 

Press, ab. Quality Entropy Heat Contents Heat of Liquid 

H q 

177.5 97.30 Sup. 1.62 1.252.2 

36 .95 1.62 1120.6 230 

1 .807 1.62 904.8 70 



15 .983 1.73 1133.6 181.3 

1 * .867 1.73 966 6 70 



36 NOTES ON POWER PLANT DESIGN 

Rankine eff. =—^7 

Hi- qi 

Hi - Hi = {Hi - gs) X Rankine Eff. = heat put into work per pound in non-conducting 

engine. 
{Hi -Hi) X cylinder eff. = heat per pound of steam actually put into work. 
1252.3 - 1120.6= 131.7 
131.7 X .45 X .93 X .92 = 50.7 .45 = cylinder eff. 

„.._ 33,000x60 
2545 =— 7y8— 

2545 X 1000 



50.7 X 746 



= 67.3 lbs. steam per K. W. hour between 177.5 and 36 lbs. ab. 



-Fn~o = 133.7 K. W. developed by the steam before it is bled. 

1133.6 - 966.6 = 167 

167 X .50 X .93 X .92 = 71.4 

A. cylinder efficiency of .5 has been used because of the moisture in the steam 
2545 X 1.34 



71.4 

_2000_ 
47.76 



= 47.76 lbs. steam per K. W. hour between 15 lbs. and 1 lb. absolute. 

= 42.0 K. W. recovered from exhaust put back at 15 lbs. ab. 

1252.3 - 904.8 = 347.5 

347.5 X 63. X .93 x .92 = 187.3 

■ 2545 X 1.34 ^ ^g_21 



187.3 

2000 - 133.7 - 42 = 1824.3 
1824.3 X 18.21 = 33,220 
Steam bled = 9,000 

Total steam to turbine from boiler = 42,220 
Total steam to condenser = 33,220 + 2,000 

While it may be allowable to use a ratio higher than .63, in this case .63 is conservative. 

Although efficiency ratios as great as 71.8 have been obtained, in general the ratio actually 
realized on the commercial machine is lower. 

By the addition of extra wheels in a stage or of extra stages it is possible to get the high ratios 
quoted, as the loss from leakage by the blades is thereby reduced, at the same time however the 
cost of the turbine is increased and it becomes a question as to whether or not the better economy 
warrants the extra expenditure due to the increased first cost. 

For low pressure turbines the efficiency ratio for machines of 50 to 75 K. W. capacity is between 
50 and 55 per cent. 

A paper read by Mr. Francis Hodgkinson before the A. S. M. E. gives the steam consumption 
of Parsons Turbines under different conditions of pressure, superheat and vacuua. 

As this data may be found useful the table has been reproduced here. 









SSSi :*- : :S2- :» 



SS5 :« 



5Slg in 



as : 



• Sc3 



S5 






.t: M i :i| is 8 



■ •« c5 



KR3 :i- K? 






cooeo 



=.S :? 



SS :S5 



: ;='3 : 



153.5 
27.0 
2.0 

3,583 


i ill 1 " 


Si 


ss' i| 


: :ss ■"■ s 


s 


148.3 
27.0 
6.0 

3,563 




g 



5t-e- ;•?)_ 



30 -O-^ • • ■— -eo 



«o -oa 



SS". :g- : 



Sg :g8 



"Si" 



5S 



S5S ■■' 



:-«■ SS :a 



149.8 

4.0 

■3,59a 


i iiS 15 ' 





,§0 .§ 


6,916 
77 


» 



:S? 



s§ 


: •" 


i :2t 




. 


■- 


iftO 

5§' 


:S| 


. -O-H 


:S 


3 





00 

5S 




: Igg 


■■£ 


S 


ka 



: :3S 



5S : "w 



o fc « 



Mo 2 ■ 

Jj-rxl ; 



: : : :S.S 

. -00 

:•= i « tt S; 

-ja 5 w *■ 0- 



SE« 



Eii'OCo 6; 



32*3 



.SB 

) « a 



^ S ^d S S ' o e Q 



•sa a 



s;: 












5S?S 



S iis is 



-- S--iS-2 



SsS ;::- S8 :"-2 






^^iS^ 



~5 :«S 



II 152 :S= 

■"' "5 Is- 



ss 



eS :«£; 



•:- || :g-: 



Si;|! 



■dS 



•sgs 



•sg 



;ss 



ssss 



'is- 



•ss- 






i ° .s. ? 



"SS.'aS 



— — ^^^ 

0000c 
J,JHB<D 



■3 
s a 



«S;Sf: 



9| 



„s- 



1 :|§-: 2 



,i S 



1- § 



S5 



S« 



a 6 



Sa S= 



5 :S= 






-Sf: 



"5:S;? 



-■ 55 



SS :S 



SS to 



-- S5e 



S8 i-^ 



S~.~ 



s i? 



^^P^ pa ioi'a*-'- i^ 

||S,;g ■S'S^Igg 1 



38 



NOTES ON POWER PLANT DESIGN 



AN ARTICLE BY A. G. CHRISTIE IN VOL. 34 A. S. M. E. TRANSACTIONS CONTAINS A TABLE GIVING 
ECONOMY TESTS OF STEAM TURBINES. THIS TABLE GIVES IN THE COLUMN MARKED 
EFFICIENCY RATIO, THE COMPARISON WITH THE RANKINS EFFICIENCY 
TABUi 2 ECONOMY TESTS Oi HIGH PRESSURE STEAM TURBINES 
EmciENCT Ratios based on Effecti^'e Horsepower Mabks & Datis Steam Tables used 



Maker of Turbine 


Type 


1 
"o 

a 


« 
•a 

as 
o 


a 


S S 
11 

1^ 


.a 
« 

of ^ 

|2 
g H 


2 

II 

S Ci 


a" 

3 

£ ^ 


S 

"3 ^ 


w 

a 

3 


.2 ra 

1^ 


S 


.2 

« 
>> 

c 

SE 


Reference 






Q 


2128 


rt 


a: 


Eh 


> 


O 


l^A 


cp 


X 


X 


H 




Erste Briinner M. F. G 


Curtis-Parsons 


1910 


1500 


156.2 


482 


27.89 


0.995 1 13.82 


16460 


247.0 


343.8 


71.8 


Periodische Mittcilungen 


Erste Brunner M. F. G 


Curtis-Parsons 




6000 


960 


184.9 


573 


28.18 


0.854 


12.56 


15570 


271.5 


380.7 


71.3 


Zeit. D.V.D. Ing., 12/10/'10 


Erste Brunner M. F. G 


Curtis-Parsons 


1910 


7442 


960 


192.0 


584 


28.18 


0.853 


12.625 


15705 


270.2 


384.4 


70.3 


Periodische Mitteilungcn 


Westinghouse Machine Co. 


Curtis-Parsons 


1910 


9173 


1800 


181.7 


433 


27.81 


1.032 


14.57 


16925 


234.1 


340.2 


68.9 


Trans. A.S.M.E., vol. 32 


Brown Boveri & Cie 


Curtis-Parsons 




3053 


1360 


150.2 


505 


29.00 


0.456 


13.01 


15990 


262.2 


385.5 


68.0 


Dinglers P.J., 6/17/'ll 


Erste Brunner M. F. G 


Curtis-Parsons 


1910 


1416 


1260 


128.2 


482 


27.60 


1.137 


15.18 


18060 


224.6 


326.5 


68.8 


Periodische Mitteilungen 


Brown Boveri & Cie 


Curtis-Parsons 


1911 


1750 


1500 


176.4 


586 


27.08 


1.392 


14.23 


17500 


239.5 


354.8 


67.5 


Zeit. F.D.G. Turb., 5/30/'ll 


Brown Boveri & Cie 


Curtis-Parsons 


1910 


3764 


1500 


161.2 


561 


28.77 


0.562 


13.04 


16290 


261.5 


391.4 


66.8 


Zeit. F.D.G. Turb., 5/30/'ll 


Westinghouse Machine Co. 


Curtis-Parsons 




9830 


750 


192.2 


475 


27.22 


1.322 


15.15 


17790 


225.2 


336.0 


67.0 


Trans. A.S.M.E., vol. 32 


Brown Boveri & Cie 


Curtis-Parsons 


1911 


1495 


3000 


200.6 


563 


26.41 


1.720 


14.78 


17880 


230.7 


345.5 


66.8 


Data from Manufacturer 


Brown Boveri & Cie 


Curtis-Parsons 


1911 


1271 


3000 


172.1 


568 


27.31 


1.278 


14.61 


17880 


233.5 


354.3 


65.9 


Data from Manufacturer 


Westinghouse Machine Co. 


Curtis-Parsons 




11466 


750 


191.7 


484 


28.07 


0.910 


14.45 


17210 


236.0 


360.5 


65.5 


Trans. A.S.M.E., vol. 32 


Erste Brunner M. F. G 


Curtis-Parsons 




1250 


3000 


184.9 


573 


27.89 


0.996 


14.32 


17680 


238.2 


373.1 


63.9 


Zeit. D.V.D. Ing., 12/10/'10 


Brown Boveri & Cie 


Curtis-Parsons 


1910 


3320 


1500 


180.9 


525 


29.02 


0.440 


13.50 


16680 


252.7 


401.3 


63.0 


Zeit. F.D.G. Turb., 5/30/'ll 


Brown Boveri & Cie 


Curtis-Parsons 




5128 


1000 


171.2 


565 


28.52 


0.726 


14.35 


17830 


237.7 


382.9 


62.1 


Stodola, 4th ed., p. 449 


Breitfield, Danek & Co 


Impulse-Parsons 


1909 


3585 


896 


160.7 


457 


28.32 


0.782 


16.08 


19070 


212.0 


352.4 


60,2 


Zeit. D.V.D. Ing., 12/10/'10 


Brown, Boveri & Cie 


Parsons 


1910 


6257 


1210 


203.7 


559 


29.02 


0.440 


11.95 


14980 


285.5 


415.0 


68.8 


Official Test Report 




Parsons 


1908 


4300 


1800 


186.4 


484 


27.96 


0.960 


14.02 


16690 


243.4 


355.7 


68 4 


Sibley Jour, of Eng.. 1/11' 
Zeit. D.V.D. log., 12/10/'10 


Brown Boveri & Cie 


Parsons 


1903 


3500 


1360 


156.4 


499 


28.84 


0.532 


13.71 


16720 


248.5 


378.6 


65.6 


Brown Boveri & Cie 


Parsons 




3000 


1360 


165.0 


625 


27.02 


1.120 


14.75 


18433 


231.3 


359.5 


64.3 


Die Turbine, 6/20/'ll 


C. A. Parsons & Co 


Parsons 




5164 


1200 


214.3 


509 


28.95 


0.473 


13.18 


16140 


258.7 


402.3 


64.3 


Stodola, 4th ed., p. 439 


Allis-Chalmers 


Parsons 


1911 


3850 


1800 


164.7 


491 


27.91 


0.983 


15.40 


18410 


221.3 348.3 1 


63.5 


Power, l/2/'12 




" 1 


A. E. G 


Curtis-Rateau 


1911 


6518 


1220 198.7 


601 


29.28 


0.352 


11.43 


14640 1 298.4 | 434.2 


68.7 


Official Test Report 
Official Test Report 


A. E. G 


Ciirtis-Ratpau 


1911 


6565 


1220 200.2 


597 


29.18 


n.40R 


11.64 


14848' 293.0 ' 427.7 


68.5 



British Westinghouse.. 

M.A.N 

Uergnaann 

Bergmann 

A.E.G 

British Westinghouse. 

A.E.G 

M. A. N 

Bergmann 



Curtis- 
Curtis- 
Curtis- 
Curtis- 
Curtis- 
Curtis- 
Curtis- 
Curtis- 
Curtis- 



Rateeu 

Zoelly 

Rateau 

Rateau 

■Rateau 

Rateau 

■Rateau 

■Zoelly 

■Rateau 



1911 

1909 
1910 
1908 
1911 
1907 

1911 



5060 
3584 
1545 
2477 
4?39 
2930 
3169 
2507 
3365 



1500 
1500 
1500 
1500 
1500 
1500 
1500 
1500 
1500 



190.2 
178.3 
188.5 
140.0 
188.3 
210.2 
184.7 
175.5 
171.0 



552 
569 
581 
522 
662 
568 
592 
460 
536 



28.68 
27.54 
28.59 
28.81 
29.11 
28.18 
29.11 
27.40 
26.00 



D.649 
1.166 
0.654 
0.588 
0.397 
0.894 
0.397 
1.234 
1.98 



13.00 
13.99 
12.97 
13.93 
11.97 
13.72 
12.74 
16.24 
15.09 



16100 
17190 
16230 
17135 
15620 
16935 
16230 
19020 
17970 



262.4 
243.7 
263.0 
244.8 
284.9 
248.7 
267.7 
210.0 
234.1 



391.5 
361.3 
396.3 
373.4 
439.0 
383.3 
425.1 
334.6 
381.3 



67.0 
67.5 
66.4 
65.6 
64.9 
64.9 
63.0 
62.8 
68.5 



Electrical Review, 6/23/'ll 
Data from Manufacturer 
Zeit. D.V.D. Ing., 12/]0/'10 
Elec. Zeit., 4/20/'ll 
Stodola, 4th ed., p. 404 
Electrical Review, 4/28/' 11 
Trans. A.S.M.E.. vol. 32 
Data from Manufacturer 
Official Test Report 



James Howden & Son. 

M.A.N 

Escher Wyss & Co. . . . 
Efcher Wyss & Co. ... 

F. Ringhoffer 

M. A. N 

Oerlilion 

Esther Wyss & Co.... 
Eacher Wyss & Co. . . . 
Escher Wyss & Co. . . . 
Escher Wyss & Co. . . . 
Escher Wyss & Co. .. . 



Zoelly 

Zoelly 

Zoelly 

Zoelly 

Zoelly 

Zoelly 

Rateau 

Zoelly 

Zoelly 

Zoelly 

Zoelly 

Zoelly 



1909 
1910 
1910 
1910 
1908 
1910 
1911 

1908 

1910 
1910 



6383 
1400 
2052 
4189 
3000 
1250 
3166 
5118 
5000 
3540 
1641 
1235 



1000 
3000 
3000 
1000 
1000 
3000 
1500 
1000 
1000 
1500 
3000 
3000 



202.7 
180.7 
193.9 
179.7 
170.7 
182.1 
213.9 
133.7 
166.4 
155.1 
221.0 
176.8 



520 
554 
585 
557 
470 
582 
663 
549 
539 
469 
672 
451 



27.33 
27.40 
28.39 
28.66 
27.60 
28.82 
29.25 
27.55 
26.38 
28.21 
27.91 
28.39 



1.269 
1.237 
0.750 
0.618 
1.138 
0.540 
0.367 
1.161 
1.736 
0.838 
0.985 
0.750 



14.305 

14.21 

13.04 

13.30 

15.52 

13.09 

11.44 

15.18 

16.13 

15.07 

13.08 

15.35 



17150 
17310 
16290 
16520 
18278 
16500 
14970 
18530 
19350 
17940 
16775 
18156 



238.5 
240.0 
261.5 
256.5 
219.8 
260.2 
298.2 
224.6 
211.2 
226.3 
260.6 
222.3 



353.0 
356.2 
392.6 
391.3 
339.2 
404.5 
450.6 
341.6 
330.4 
349.5 
406.5 
357.8 



67.5 
67.4 
66.6 
65.5 
64.8 
64.4 
66.1 
65.7 
63.9 
64.8 
64.1 
62.2 



Engineer, London, 10/29/'O9 
Zeit. D.V.D. Ing., 12/10/'10 
Zeit. F.D.G. Turb., 2/20/'ll 
Zeit. F.D.G. Turb., 2/20/'ll 
Zeit. D.V.D. Ing., 12/10/'10 
Zeit. D.V.D. Ing., 12/10/'10 
Engineering, 10/20/'10 
Dinglers P. J., 7/15/'ll 
Zeit. D.V.D. Ing., 12/10/'10 
Dinglers P. J.. 7/15/'ll 
Zeit. F.D.G. Turb., 2/20/'ll 
Zeit. F.D.G. Turb., 2/20/'ll 



British Thomson-Houston 

Gen. Elec. Co 

British Thomson-Houston 

A.E.G 

A. E. G 

Gen. Elec. Co 

British Thomson-Houston 

Gen. Elec. Co 

Gen. Elec. Co 

British Thomson-Houston 
Gen. Elec. Co 



Curtis 
Curtis 
Curtis 
Curtis 
Curtis 
Curtis 
Curtis 
Curtis 
Curtis 
Curtis 
Curtis 



1911 

1909 
1906 
1909 

1911 



1911 
1910 



2987 
3464 
2500 
3000 
2236 
8880 
1541 
10816 
5095 
1221 
8775 



1500 

1500 
1500 
1500 

1500 
750 

3000 
750 



154.7 
210.0 
126.5 
191.3 
191.6 
192.5 
149.7 
190.0 
185.1 
134.7 
194.0 



505 
513 
414 
590 
654 
487 
365 
525 
554 
448 
451 



26.75 
28.75 
28.47 
29.05 
29.34 
28.02 
27.97 
29.39 
29.40 
27.16 
27.95 



1.557 
0.575 
0.711 
0.427 
0.284 
0.933 
0.956 
0.260 
0.255 
1.353 
0.956 



15.96 
13.62 
15.92 
12.79 
11.77 
15.05 
17.46 
12.90 
12.71 
17.75 
15.95 



18960 
16620 
18590 
16240 
15450 
17965 
19720 
16135 
16090 
20690 
18720 



213.7 
250.4 
214.0 
266.6 
289.8 
226.7 
195.3 
264.5 
268.4 
192.2 
213.8 



321.2 
393.4 
336.1 
420.4 
455.8 
359.5 
320.2 
427.3 
436.0 
■314.0 
350.8 



66.5 
63.6 
63.7 
63.4 
63.6 
63.1 
61.0 
61.9 
61.6 
61.2 
61.0 



Engineering, 10/20/'ll 
Trans. A.S.M.E., vol. 32 
Zeit. D.V.D. Ing., 12/10/'10 
Zeit. D.V.D. Ing., 12/10/'10 
Zeit. D.V.D. Ing., 12/10/'10 
Trans. A.S.M.E., vol. 32 
Engineering, 10/20/'ll 
Trans. A.S.M.E., vol. 32 
Trans. A.S.M.E., vol. 32 
Engineering, 10/20 ''11 
Trans. A.S.M.E., vol. 32 



References: 



Zeit. D.V.D. Ing. — Zeitschrift des Vereines Deutscher Ingenieure; Zeit. F.D.G. Turb. — Zeitschrift f tlr das Oesammtw Tuibinenwesen; 
Dinglers P.J. — Dinglers Polytechnisches Journal; Elec. Zeit. — Electrotechnische Zeitschrift. 



Il 



NOTES ON POWER PLANT DESIGN 

A 



39 



Discharge^ 



£')chausi- 




Port/a/ £'nd and S/cfe E/ei/af/ons. 

•5hoiv/nff change /n stsarn 
connection /n .sizes: — 

/80-360 Sai. joer min 
J"^ ^Sfeam 360 -S^O •• 




£nd and 3/c/e £'/ek'ai-/ons:— 90 -/80 Gcf/.per m. 



Partial End and Sids Elei^ations, 

3 halving change in ^team 
connection in sizss ■' — 

S'^O-IZO Sai.permin 

720 -i20O " 




Gcr/. per m in. 


90-180 


/ao-360 


360-S40 


540-720 


720 -/20C 


1) 


j' 




4-k" 


9" 






A 


a -ig 


3--7i- 


8'-6^' 


ll'-9ji" 


12' -/O^' 


i/" 








'y£ 


II" 


B 


2'-S" 


2'-S" 


3'- 1" 


4-'-7" 


-#•'-7" 


Exhaust dia. 


4" 


4" 


6" 


9" 


id' 


C~ 


,9i" 






2--8f 


3'-4-i" 


K 


i4' 


J4-" 


ei 


iSg 


17" 


D 


2'-///' 


3'-z" 


3'-6f 


S'-3^" 


4-'-/o" 


L 


22" 


23^ 


2'-2k" 


3-1" 


3-1" 


E 


2 '-6/" 




2'-'04' 


4-'-2f: 


4'-oi" 


i^ 


< 


764:" 


78^" 


2'-4" 


2'-&" 


F 


ae" 


z-^i 


24^ 


3'-0" 


2'-8^' 


1 


Suction dia. 


4" 


s" 


s" 


6" 


s" 


1 

_ 


Jfeom dia 


z" 


z' 


3i" 


^i" 


3S" 


N 


7/ 


iif 


iif 


/&" 


iSi" 


6 


6/ 










O 


i9i' 


'&ra 


^eg 


20" 


2'i" 


G' 




^4' 


'^r 


'7i' 


'^i' 


Discharge dia. 


3" 


4" 


4-" 


s" 


6" 


H 


"g" 


"f 


'^k- 


- 




P 


^$ 


7^' 


^" 


iof 


lO" 


h' 








24" 


2-3^" 


Q 


'S^" 


24'M' 


^^.r 


2-4,r 


3'-Sf 


J 


s" 










P 


//" 


i2i" 


'2s" 


i6s" 


22" 






5 


■^-^i" 


^'-sM' 


s-ef 


y'-'Og 


8'-3i' 






T 


23^ 


<?/i" 


2',i' 


2'-lii" 


2'-8f 






U 


12^' 


I4-" 


■ '^ii' 


2'i" 


2'i" 






K 


^'-^i' 


l^-^#' 


y-^f 


4-0.^" 


4'-or 



40 NOTES ON POWER PLANT DESIGN 



BLEEDING STEAM 

In many cases where efficiency is based on coal a higher plant economy may be obtained by 
bleed ing some of the steam from one of the low pressure stages and using this steam to heat the feed 
water instead of passing all of the steam through the engine or turbine. If there is a considerable 
amount of auxiliary steam available to heat the feed water, there will in general, be no need of bleed- 
ing steam from one of the stages, as the auxiliaries will usually furnish enough exhaust to raise 
the temperature of the feed water. In some pumping stations, however, where the circulating 
water passing through the condenser does not have to be pumped by a special pump, the number 
of auxiliaries in use is reduced and the steam available for heating the feed water is small in amount. 
In such cases it may be advisable to bleed steam from one of the stages where the pressure is approx- 
imately 5 lbs. above the atmosphere. The equation^ for calculating efficiency where steam is bled 
and where steam is not bled, follow: The percentage to be bled may be anywhere from 2 to as much 
as 10 per cent depending upon conditions. The temperature of the feed water cannot of course, 
be heated to a higher temperature than that of the steam bled from the turbine. 

Subscript 1 = boiler condition. 

qi + XiTi = Hi 
Subscript 2 = condition at lowest back pressure or pressure in condenser. 

92 + iC2r2= Hi 
Subscript b = condition at point where bleeding takes place. 
qs + Xbn = Hb 

W = total steam per H. P. hour, different in amount for Cases A and B. 
B = Steam bled per H. P. hour. 
W — B = Steam through condenser per H. P. hour. 

Qh = heat of liquid of condensed steam leaving condenser. 

This water is about 7 degrees lower than the temperature corresponding to the vacuum in 
condenser. 

q/ = heat of liquid of feed water. 

Assume 60 per cent cylinder efficiency. 

Case A 

No Steam Bled 

2545 H- .60 {Hi - Hi) = steam per H. P. hour to be supplied by boiler. 

.00 {Hi — Hi) = heat transformed into work per pound of steam supplied. 

Case B 

Some Steam Bled from One of the Later Stages and Utilized to Heat 

the Feed Water 

r.e^c r^^ P^r ccut through turbine to condenser x {Hi- Hi) 
2545 ^ .60 I ^ 

^ Per cent bled (g.-H,) | ^j^^_ ^^^^^ ^^^ ^ p ^^^^ ^ ^ 
Per cent through ,„ ,, , Per cent bled ,tt tt \ \ -d -t. tt u- u 

1 loo — ^^' ~ -^ "•" — ~loo — ^ ' '' \ ^ ^^^ 

transformed into work per pound of steam. 






NOTES ON POWER PLANT DESIGN 41 

W (Hi - q/) = B. T. U. per H. P. hour to be supplied by the boiler. 

2,545 



Efficiency Case B = 



W (Hi - Qf) 



{W - B) (qf - qn) = b(h, - .6 (H, - Hb) - qj) 
Wqf = {W - B) qh + B (Hb) + .40 (Ht - Hb) X B 

2545 
Therefore efficiency Case B 



WHi - {W - B) qh - BHb - .40 B {H, - Hb) 
2545 



W (Hi - qh) 



Efficiency Case A = 

B. T. U. put into work per pound of steam. 
Case A .60 (Hi - H2) 

CaseB -l^^l^^-^^^ ^H, - H,)-^^^'^ (Hr - H,) 
(1) Difference A-B .60 | i-%^ip^ 1 (^, _ h,) - -^^^f"^ (H^-Hb) 
Case A utilizes per lb. ^ {Hb — H2) more heat units than Case B. 



The heat to be supplied by the boiler per pound is 

Case A= Hi - qh " \ 

P««^-R R n n n %through .40% bled , %bled 
Case )i = Hx- qf q/= qn ^qq ' iqo '^ ~ ''' "' 100 

« 

Case B = Hi - % ^jpA. g.-^^^^A (^, _ Hb) -^^^Hb 

(2) Case A - Case B = {^^^P"^- D Q.+ --|^- (H. - Hb) + %^>^ - Hb 

.40% bled r. X % bled %bled 

(^ 1 - iifc) -TRTT- qh + —TT^TT- tib 



100 ' ' "' 100 ^" ' 100 

'- — ^^ (Hi -Hb) -I 'TncT' (Hb ~ Ih) which is the difference in the heat supplied 

by the boiler per pound of steam 



42 NOTES ON POWER PLANT DESIGN 

GENERAL DIMENSIONS OF ENGINES 

Tables of cylinder sizes, horse power and overall dimensions of a number of different engines 
are given on the pages following. 

The engines shown are each typical of a class and have been selected with this in mind only. 
In general the single cylinder engines are rated on a cut-off at about one quarter stroke. 



NOTES ON POWER PLANT DESIGN 
WATER RATES OF SMALL TURBINES 



43 



The water rates of small turbines, exhausting against atmospheric pressure, based on test are shown by the 
accompanying plots taken from an Article by G. A. Orrok in Vol. .31 of Transactions of A. S. M. E. 



5000-1 10000 




120" 160 

Brake Horse Power 



Steam Consumption Cuhves, Bliss Turbine, Non-Condensing 




83 100 120 
Brake Horse Power 



TESTED BY F. L. PRTOR AT HOBOKEN, N. /. 

O = Two-nozzle, X = Four-nozzle 



1500 




Load CtmvES of Kerr Turbine 

24-IN. WHEEL, 8-8TAOB 175-I-B. OAQE PEE88UEE, NON-CONDBNSIN<J 



16000 



10 15 

Brake Horse Power 




3000 P 



1000 



100 150 

Brake Horse Power 



Steam Consumption Curves, Sturtevant Turbine 

20-IN. WHEEL, 8INGLE-BTAGE, NON-CONOENSINO, 2400 R.P.M. 

70 




Steam Consumption Curves, 24-in. Kerr Turbine 

SIX-STAGE, CONDENSING, VARYING VACUUM, 70-LB. GAGE PBESBURB 
3500 



10 20 30 40 50 60 70 

Brake Horse Power 

Steam Consumption Curves, Terry Turbinb 

24-IN. WHBEI,, 150-LB. PBESSUSE, NO SUPERHEAT, NON-CONDENSING. TESTED BY WE8TINGHOU8E 
MACHINE CO., PITTSBUBa, PA. 




2e 30 40 50 

Brake Horse Power 



60 



Steam Consumption Curves, 50 h.p. Curtis Turbine 

ONE-PHESSDRE-STAGE, THREE ROWS OF BUCKETS, 25J-IN. WHEEL, CURVES CORRECTED TO 
150-LB. BOILER PRESSURE, NO SUPERHEAT, ATMOSPHERIC EXHAUST 




liX) 200 

Turbine Brake Horse Power 

Steam Consumption Curves, 200-h.p. Curtis Turbine 

THREE-STAGE, .36-I^f. WHEEL, CORRECTED TO 165-LB. ABB. BOILER PBES8URB, NO SUPERHEAT, 

NON-CONDENSING 



80 



60 



50 



tf 40 



20 



Curve 



Type 



A 


Sturtevant 


2,400 


B 


Terry 


2,350 


C 


Bliss 


2,600 


c. 


'■' 


2,000 


D 


Kerr 


2,800 


E 


Curtis 


3,600 


E' 


" 


2,000 



K.P.M. Rated H.P. 
20 
50 
100 
200 
150 
50 
200 



Steam Press.— 150 Lb. 
Dry Steam 
Atmospheric Exhaust 




Load 
Economy Curves of Small Turbines 



NOTES ON POWER PLANT DESIGN 



45 



SKINNER CENTRE CRANK AUTOMATIC 
OILING ENGINE 






Maxim'm 
Rating. 


Constant. 


WHEELS. 


Diimeter of 
Pipes. 


FLOOR Space. 
Belted. 


FLOOR Space. 
Direct Connected. 


Kilowatt 


SIZE OF 


Diam. 
Inches. 


Belt 
Pulley 
Width. 
Inches. 


CAPACITY 


ENGINE. 


Steam. 
Inches. 


Exhaust. 
Inches. 


Length. 
Ft. Ins. 


Width. 
Ft. Ins- 


J_ength. 
Ft. Ins. 


Width. 
Ft. Ins. 


OF 

DYNAMO. 


8 xlO 


55 


.00253 


48 


9 


2X 


3 


7 


7 


4 


9 


7 7 


6 


10 


20— 30 


9 xlO 


60 


.00321 


48 


9 


3 


3X 


7 


7 


4 


9 


7 7 


7 




25— 35 


10 xlO 


70 


.00396 


54 


11 


3X 


4 


8 


7 




10 


8 8 


7 


2 


35— 40 


11 xlO 


80 


.00479 


54 


11 


3X 


4 


8 


7 




10 


8 8 


7 


5 


40— 45 


8 xl2 


55 


.00304 


48 


9 


2X 


3 


7 


8 


4 10 


7 8 


6 


10 


20— 30 


9 xl2 


60 


.00385 


48 


9 


3 


3% 


7 


8 




10 


7 9 


7 


4 


25— 35 


10 xl2 


70 


.00476 


54 


11 


3X 


4 


8 


8 




11 


8 8 


7 


4 


35—40 


11 xl2 


80 


.00575 


54 


11 


3X 


4 


8 


8 




11 


8 9 


7 


5 


40— 50 


ll^x 12 


80 


.00629 


54 


11 


3% 


4 


8 


8 




11 


8 9 


7 


9 


45— 50 


12 xl2 


100 


.00685 


60 


13 


4 


5 


10 




5 


1 


10 6 


8 


4 


50— 60 


13 xl2 


135 


.00804 


60 


13 


4X 


6 


10 


1 


5 


2 


10 7 


8 


6 


60— 75 


14 xl2 


135 


.00932 


60 


1.3 


4% 


6 


10 


1 


5 


2 


10 7 


8 


6 


60— 75 


10 xl5 


80 


.00595 


60 


13 


3X 


4X 


10 




5 


1 


10 6 


8 


4 


50 


11 xlo 


80 


.00719 


60 


13 


3X 


4% 


10 




5 


1 


10 6 


8 


4 


50 


12 xl5 


100 


.00856 


60 


13 


4 


5 


10 




5 


1 


10 6 


8 


4 


50 


13 xl5 


135 


.01005 


60 


13 


4% 


6 


10 


1 


5 


2 


10 7 


8 


6 


60— 75 


14 xlo 


135 


.01166 


60 


13 


4% 


6 


10 


1 


5 


2 


.10 7 


8 


6 


60— 75 


15 xl6 


180 


.01427 


66 


15 


5 


6 


12 




6 


8 


12 7 


10 


4 


lOO 


16 xl6 


180 


.01624 


66 


15 


5 


6 


12 




6 


8 


12 7 


10 


4 


100 


17 xl6 


200 


.01833 


66 


15 


5 


6 


12 




6 


8 


12 7 


10 


4 


100—125 


18 xl6 


270 


.02055 


78 


17 


6 


8 


13 


6 


7 


4 


14 9 


11 


3 


125—150 


12 xlS 


120 


.01028 


72 


14X 


4 


5 


12 


1 


■ 6 


6 


12 5 


10 




75 


14 xl8 


140 


.01399 


72 


14X 


4X 


6 


12 


1 


6 


6 


12 5 


10 




75 


15 xl8 


180 


.01606 


72 


16% 


5 


6 


12 


3 


6 


10 


12 7 


10 


4 


100 


16 xl8 


180 


.01827 


72 


16% 


5 


6 


12 


3 


6 


10 


12 7 


10 


4 


100 


17 xl8 


200 


.02063 


72 


16X 


5 


6 


12 


3 


6 10 


12 7 


10 


4 


100—125 


18 xl8 


280 


.02313 


78 


19 


6 


8 


13 


6 


7 


6 


14 9 


11 


S 


125—150 


19 xl8 


280 


.02577 


78 


19 


6 


8 


13 


6 


7 


6 


14 9 


11 


5 


150 


20 xl8 . 


280 


.02856 


78 


19 


6 


8 


13 


6 


7 


e 


14 11 


11 


7 


150—175 


18 x20 


300 


.0257 


84 


21 


6 


8 


14 10 


8 


5 


16 6 


12 


10 


17.5—200 


19 x20 


300 


.02863 


84 


21 


6 


8 


14 10 


8 


5 


16 6 


12 10 


176—200 


20 x20 


300 


.03173 


84 


2i 


6 


8 


14 


10 


8 


5 


16 6 


12 


10 


175—200 


21 x20 


350 


.03498 


84 


23 


7 


10 


14 


11 


8 


7 


16 10 


12 


11 


200 


22 x20 


350 


.03839 


84 


23 


7 


10 


14 11 


8 


7 


16 10 


12 


11 


20O 


18 x24 


300 


.03084 


84 


21 


6 


8 


15 


3 


8 


6 


17 2 


11 


6 


175—200 


19 x24 


300 


.03436 


84 


21 


6 


8 


15 


3 


8 


6 


17 2 


11 


6 


175—200 


20 x24 


320 


.03808 


84 


21 


6 


8 


15 


3 


8 


6 


17 2 


11 


6 


200 


21 x24 


350 


.04198 


84 


24 


7 


10 


15 


4 


B 


9 


17 4 


11 


8 


200 


22 x24 


350 


.04607 


84 


24 


7 


10 


15 


4 


8 


9 


17 4 


U 


8 


200 



46 



NOTES ON POWER PLANT DESIGN 
SKINNER ENGINE 



SIZE OF 


Revolutions 

per 

Minute. 


INITIAL PRESSURES. 


SIZE OF 
ENGINE. 


Revolutions 

per 

Minute. 


INITIAL PRESSURES. 


ENGINE. 


70 


80 


eo 


100 


110 


120 


70 


80 


so 


lOO 


no 


120 


8 xlO 


300 
326 
350 


27 
29 
31 


31 
33 
36 


34 
37 
40 


38 
41 
44 


42 
45 
49 


46 
50 
53 


13x12 


250 
275 
300 


70 

77 
84 


80 
89 
97 


91 
100 
109 


101 
111 
121 


111 
122 
133 


121 
133 


9 xlO 


300 
326 
350 


34 
37 
39 


39 
42 
45 


43 
47 
61 


48 
62 
56 


53 
57 
62 


58 
63 


14x12 


250 
275 
300 


82 
90 
99 


93 
103 
112 


105 
115 
126 


117 
128 
140 


128 
141 


140 


10 xlO 


300 
325 
350 


42 

45 
49 


48 
52 
66 


.54 
58 
62 


60 
64 
69 


66 
71 


71 


10x15 


226 
250 
276 


47 
52 
57 


54 

go 

66 


60 
67 
74 


67 
74 
82 


74 
82 


80 


11 xlO 


300 
325 
350 


50 
55 
59 


68 
62 
67 


65 
70 
76 


72 
78 
84 


79 
86 


86 


11x15 


225 
250 

275 


57 
63 
69 


65 
72 
79 


73 
81 
89 


81 
90 


89 




8 xl2 


250 
275 
300 


27 
29 
32 


31 
34 
37 


34 
38 
41 


38 
42 
46 


42 
46 
60 


46 
60 
66 


12x15 


225 
250 
275 


67 
75 
83 


77 
86 
94 


87 

96 

106 


96 
107 


106 




9 xl2 


250 
275 
300 


34 
37 
41 


39 
42 
46 


43 

48 
62 


48 
53 
58 


63 
58 
64 


68 
64 


13 X 15 


225 
250 
275 


79 
88 
97 


90 
101 
111 


102 
113 
124 


113 
126 
138 


124 
138 


136 


10 xl2 


250 
275 
300 


42 
46 
50 


48 
52 
57 


54 
59 
64 


60 
66 
71 


66 

72 


71 


14 X 15 


225 
250 
275 


92 
102 
112 


105 
117 
128 


118 
131 
144 


131 
146 
160 


144 
160 


157 


■11 xl2 


250 
275 
300 


50 
55 
60 


58 
04 
69 


65 
71 
78 


72 
79 
80 


79 
87 


86 


15x10 


210 
230 
250 


105 
116 
125 


120 
131 
143 


135 
148 
161 


150 
164 
178 


166 
181 


180 


11^x12 


250 
276 
300 


55 
61 
66 


63 
69 
76 


71 

78 
85 


79 
87 


87 




10 x 10 


210 
230 
250 


119 
131 
142 


136 
149 
162 


154 
168. 
183 


171 
187 
203 


188 
206 


205 


12 xl2 


250 
275 
300 


60 
66 
72 


69 

75 
82 


77 
85 
93 


86 

94 

103 


94 
104 


103 


17x10 


210 
230 
250 


135 
148 
160 


154 
169 
183 


173 
190 
206 


193 
211 
229 


212 
232 


231 


18 X IG 


210 
230 
250 


150 

165 
180 


173 
189 
206 


194 
213 
231 


210 
236 
257 


237 
200 
283 


259 
284 


19x20 


160 
180 
200 


160 
180 
200 


183 
206 
229 


206 
232 

258 


229 • 

258 

286 


252 
283 
315 


275 
809 


12 X 18 


175 
200 
225 


03 
72 
81 


72 
82 
93 


81 

93 

104 


90 
103 
116 


99 
113 
127 


108 
123 


20x20 


160 
180 
200 


178 
200 
222 


203 
229 
254 


229 
257 
286 


254 
286 
317 


279 
314 


306 


14 X 18 


175 
200 
225 


86 

98 

110 


98 
112 
126 


110 
126 
142 


122 
140 
157 


135 
154 


147 


21x20 


160 
180 
200 


196 
220 
245 


224 
252 
280 


252 
283 
315 


280 
315 
350 


308 

346 


336 


15 X 18 


175 
200 
225 


98 
112 

127 


113 
129 
145 


127 
145 
163 


141 
161 
181 


155 
177 


169 


22x20 


100 
180 
200 


215 
242 
269 


246 
276 
307 


276 
311 
346 


307 
346 
384 


338 
380 


369 


IG X 18 


175 
200 
225 


112 
128 
144 


128 
146 
165 


144 
165 
185 


J 60 
183 
206 


170 
201 


192 


18x24 


140 
150 
165 


151 
162 

178 


173 

185 
204 


194 
208 
229 


216 
231 
255 


237 
254 
280 


259 
278 
305 


17 X 18 


175 
200 
225 


126 
144 
162 


144 

165 
186 


163 
186 
209 


181 
206 
232 


199 
227 


210 


19x24 


140 
150 
165 


168 
180 
198 


192 
206 
227 


217 
232 
255 


241 
258 
284 


205 
284 
312 


289 
309 


18 X 18 


175 
200 
225 


142 
162 
182 


162 
185 
208 


182 
208 
234 


202 
231 
200 


223 
254 
286 


243 

278 


20x24 ■ 


140 
150 
165 


187 
200 
220 


213 
229 
251 


240 

257 
283 


267 
286r 
314 


293 
314 


320 


19 X 18 


175 
200 
225 


158 
180 
203 


180 
206 
232 


203 
232 
261 


226 
258 
290 


248 
284 


271 


21x24 


140 
150 
165 


206 
220 
242 


235 
252 

277 


265 
283 
312 


294 
316 
346 


323 
340 


352 


20 X 18 


175 
200 
225 


175 
200 
225 


200 
229 
257 


226 
257 
289 


250 
286 


275 




22x24 


140 
150 
165 


226 
242 
266 


258 
276 
304 


290 
311 
342 


323 
346 
380 


365 
380 


387 


18 X 20 


160 
180 
200 


144 
162 
180 


165 
185 
206 


185 
208 
231 


206 
231 
257 


226 
254 
283 


247 
278 
308 


18 X 24 — 22 x 24, Side Crank only. 
18 X 20 — 22 X 20, Center Crank only. 
All others, Side or Center Crank. 



NOTES ON POWER PLANT DESIGN 



47 



AMERICAN BALL DUPLEX COMPOUND ENGINE 
FOR DIRECT CONNECTED SERVICE 





Horse- 
power 


K.W. 


Cylinder 

Diameters and 

Stroke 


Revolutions 

per 

Minute 


General Dimensions in Jtnches 


Shipping Weight 
in Pounds 


Floor Spa'ce 


Wheels 


C 


D 


E 


F 


H 


Steam nnd 
Exhaust Pipes 


Direct- 
con- 
nected 
Engine 


Engine 

and 
Dynamo 


Leiigth 


Width 


Dia. 

A 


Width 
B 


Steam 


Exhaust 


80 
120 
160 
200 
250 
325 
400 


50 
75 
100 
125 
150 
200 
250 


9K&15 X 11 
llK&18Kxl2 

13 & 20 X 14 

14 & 22 X 16 
16 & 25 X 16 
18 & 28 X 18 
20 & 33 X 18 


275 to 300 
260 to 290 
240 to 260 
320 to 340 
2i0 to 230 
190 to 210 
180 to 300 


130;^ 

144X 

157 

164X 

179-4 

184 


94^ 
109'A 
lUK 
135j^- 

147 
157 


60 
66 

72 
•78 
84 
84 
90 


11 

13 
15 
17 
19 
23 
25 


16 
18 

20K 
21 >^ 

26 

38 


34^ 

39 

43X- 

46X 

4SU 

54 

57 


STA 

108X 
118 
123K 
137 K 
139 


35;^ 

38;^ 

•43;^ 

45 

45. 

45 

48 


27;^ 

33 

43 
49 
54 


S/2 

4 

5 
6 
6 

7 


5 
6 
7 
8 
9 
10 
12 


11,600 
15.350 
31,500 
24,500 
31,700 
39,500 
48,000 


19,800 
25,350 
33,100 
39,300 
48,200 



Note— The cylinders mentioned in this table are adapted for 100 pounds steam pressure, non-condensing. For other conditions the cylinders-- 
will he varied to give best economy. 



48 



NOTES ON POWER PLANT DESIGN 



THE AJAX ENGINE, MADE BY HEWES & PHILLIPS 

NON RELEASING CORLISS VALVE GEAR FOR DIRECT 

CONNECTING UNITS 






tial Pressure 
n Pounds 

125 1 '5° 


Size of 
Engine 


Revo- 
lutions 


Initial Pres! 


ure 
s 

150 


Diameter 


Pu 


ley 


Cubic 
Feet in 


Approximate 

Floor Space 

lielted 


From 
Center ot 
Engine to 
Center of 

Back 


From 
Center of 
Crank-shaft 
to end of 


From 
Center of 

Engine to 
Floor 


Con- 
stant 




in Pound 
.00 1 ,25 






Dia- 




Based 


lOO 










on I 
















Steam 


Exhaust 


meter 


Face 


Foundation 


Length 


Width 


Bearing 


Cylinder 




Pound 
M. E. P. 




kilowatts 




Inches 




Horse-power 


Inches 


Inches 


Inches 


Inches 




Ft. 


Ins. 


Ft. 


Ins. 


Ft. Ins. 


Ft. Ins. 


Ft. Ins. 


I Rev. 


58 


72 


88 


12 X 15 


225 


86 


108 


132 


4'A 


6 


72 


16 


252 


II 


7 


6 





4 6 


8 


21 


.0085 


66 


85 


104 


13 X 15 


225 


100 


127 


156 


5 


6 


72 


16 


260 


II 


7 


6 





4 6 


S 


21 


.0100 


73 


91 


112 


'3>^xi5 


225 


IIO 


'37 


168 


5 


6 


72 


16 


260 


I I 


7 


6 





4 6 


I 3 


21 


.0108 


79 


95 


120 


14 XI5 


225 


118 


147 


181 


5 


6 


72 


16 


270 


I I 


8 


6 




5 


8 3 


21 


.0116 


83 


los 


129 


I4>^xi5 


225 


125 


157 


'93 


5 


6 


72 


16 


270 


1 I 


8 


6 




5 


? 5 


21 


.0124 


90 


"3 


140 


'5 X15 


225 


135 


170 


210 


6 


7 


72 


16 


280 


I I 


10 


6 




5 I 


^ 5 


21 


.0134 


100 


1-9 


160 


16 X 15 


225 


150 


193 


237 


6 


7 


72 


16 


280 


11 


10 


6 




5 ' 


S S 


21 


.0152 


83 


105 


129 


14 X 16 


225 


125 


'57 


'93 


6 


7 


72 


16 


270 


II 


8 


6 




5 


9 


21 


.0124 


90 


112 


'38 


H}4xi6 


225 


■35 


169 


207 


6 


7 


72 


16 


270 


I I 


8 


6 




5 0. 


9 


21 


•o'33 


96 


120 


150 


15 X 16 


225 


145 


181 


223 


6 


7 


72 


16 


290 


I I 


10 


6 




5 ' 


9 2 


21 


.0143 


106 


136 


.67 


i6 X 16 


225 


160 


204 


251 


6 


7 


72 


18 


290 


II 


10 


6 


9 


5 2 


9 2 


21 


.0161 


123 


'54 


190 


17 X 16 


225 


185 


23' 


286 


6 


7 


73 


iS 


290 


I I 


10 


6 


9 


1 - 


9 4 


21 


0183 


"3 


'43 


'73 


16 X 18 


210 


170 


215 


265 


6 


7 


78 


20 


300 


■3 


5 


7 


7 


6 


9 6 


21 


.0182 


130 


162 


200 


17 X 18 


210 


'95 


244 


300 


6 


7 


78 


22 


320 


■3 


5 


7 


9 


6 I 


9 6 


21 


0206 


'43 


181 


223 


i8 X18 


210 


215 


272 


335 


6 


7 


78 


24 


330 


'3 


5 


7 


1 1 


6 3 


9 8 


2 I 


.0230 


160 


202 


269 


19 X18 


210 


240 


3°4 


404 


7 


8 


78 


26 


360 


'3 




8 


10 


7 


9 8 


2 I 


.0257 


178 


225 


276 


20 X 18 


210 


268 


338 


415 


7 


8 


78 


28 


420 


'3 


8 


9 





7 3 


9 10 


2 I 


.0285 


130 


162 


200 


17 X 19 


200 


■95 


245 


301 


6 


7 


84 


24 


430 


13 


1 1 


7 


II 


^' ^ 


10 


2 I 


.0217 


150 


182 


225 


18 X 19 


200 


220 


274 


337 


6 


7 


84 


25 


440 


13 


1 1 


8 





(> 3. 


10 


2 I 


.0243 


160 


204 


251 


19 X19 


200 


240 


306 


376 


7 


8 


84 


26 


450 


'3 


1 1 


8 


10 


7 


10 2 


2 I 


.0271 


180 


226 


278 


20 X 19 


200 


270 


340 


418 


7 


8 


84 


26 


460 


'3 


II 


S 


10 


7 


10 6 


2 I 


.0301 


'53 


192 


236 


18 X 20 


200 


230 


289 


355 


6 


7 


84 


26 


470 


'4 


10 


8 


2 


6 5 


10 8 


2 I 


.0256 


170 


215 


264 


19 X 20 


200 


25s 


322 


396 


6 


7 


84 


28 


480 


'4 


10 


9 





7- 3 


10 S 




.0285 


190 


238 


293 


20 X 20 


200 


285 


358 


440 


7 


8 


84 


3° 


500 


14 


10 


9 


2 


7 4 


10 10 




.0317 


206 


262 


323 


21 X 20 


200 


310 


394 


485 


7 


8 


84 


32 


500 


14 


10 


9 


2 


7 4 


1 1 


2 I 


•0349 



Horse-power. — In the computation of the power of an engine, the prime factors are area of cylinder, pressure of steam, piston speed, and point at which 
steam is cut off. Our calculations of horse-power, as indicated in the above table, are based upon an initial steam pressure of 100, 125 and 150 pounds per square 
inch, valve gear cutting off at ^ stroke, piston speed varying from 562 feet for the smallest up to 666 for the largest, size. These conditions can be changed, and 
by increasing one or all, the power of an engine is increased in like proportion. 



NOTES ON POWER PLANT DESIGN 



49 



HEWES & PHILLIPS HEAVY DUTY 
CROSS COMPOUND CORLISS ENGINE — TANGYE TYPE 




Dimensions of 
Cylinder 


I 


and Wliee 


s 


Horse-power 80 Lbs. 

Initial Pressure 

% Cut-oH 


Horse-power 90 Lbs. 

Initial Pressure 

% Cut-off 


Horse-power too Lbs. 

Initial Pressure 

K Cut-off 


Size of Quadrangle 

witliin which Engine 

ii-.cluding Fly-wheel 

will stand 


Length of 

Crank-shaft 

from Outside 

of Main 

I3earhig5 


Distance 

from Center 

of Crankshaft 

to End of 

Cylinder 


Height from 

Base-plate Ho 
to Center of C 

Crankshaft B 
Pc 


se -power 
onstant 
ased on 

und M. 
P.. I Rev. 


Bore 


Stroke 


Diameter 


Face 


Weight 


Revs, per 


Horse- 


Revs, per 


Horse- 


Revs, per 


Horse- 


Length 


Width 


E. 


in Inches 


in inches 


in Feet 


in Inches 


in Pounds 


Minute 


power 


Minute 


power 


Minute 


power 


Ft. Ins. 


Ft. Ins. 


Ft. Ins. 


Ft. Ins. 


Ft. Ins. 




10 


24 


6 


12 


4000 


125 


5° 


125 


55 


125 


62 ■ 


'3 I 


5 " 


5 2rV 


10 I 


I II 


0094 


12 


24 


7 


14 


5000 


125 


75 


125 


84 


125 


93 


14 1 1 


6 9 


5 3 


10 II 


I II 


0137 


12 


30 


8 


'4 


6coo 


120 


85 


120 


94 


120 


104 


16 II 


6 9 


5 2i3 


12 II 


I II 


017I 


14 


30 


8 


18 


7000 


120 


'■5 


120 


125 


120 


'37 


17 7 


7 7 


5 '0^ 


13 ' 


2 I 


0230 


U 


36 


9 


18 


Sooo 


) 10 


126 


I 10 


'43 


I 10 


160 


'9 7 


7 7 


5 ^0% 


15 I 


2 I 


0276 


i6 


30 


10 


20 


9000 


120 


'5' 


120 


170 


120 


190 


iS 5 


8 8 


6 6 


13 5 


2 3 


0301 


:6 


36 


10 


24 


1 0000 


I 10 


166 


I 10 


190 


I 10 


2'3 


20 5 


8 8 


6 6 


■5 5 


2 3 


0361 


i6 


42 


12 


24 


10600 


100 


177 


100 


200 


100 


S26 


23 5 


8 8 


6 6 


'7 5 


2 3 


0421 


i8 


36 


12 


26 


12000 


I 10 


210 


I 10 


240 


7 10 


270 


21 6. 


9 5 


8 3rV 


15 6 


2 5 


0457 


i8 


42 


14 


28 


14000 


100 


2^3 


100 


255 


100 


287 


24 6 


9 5 


8 3tV 


17 6 


2 5 


0533 


20 


36 


12 


28 


I4OCO 


I 10 


236 


no 


270 


110 


305 


22 II 


10 3 


8 8'A 


15 II 


2 6 


0564 


20 


42 


'4 


30 


17000 


100 


275 


100 


3'5 


100 


355 


24 II 


10 3 


8 S'A 


17 II 


2 6 


0658 


20 


48 


16 


3j 


19000 


90 


2S4 


90 


3^5 


90 


365 


27 II 


'0 3 


8 S'/, 


19 1 1 


2 6 


°753 


22 


42 


16 


36 


21000 


100 


334 


100 


382 


100 


422 


26 2 


1 1 I 


'0 3 


18 2 


2 9 


0797 


22 


48 


16 


38 


23000 


90 


344 


90 


393 


90 


442 


28 2 


II I 


10 3 


20 2 


2 9 


0911 


22 


54 


16 


40 


25000 


So 


344 


So 


395 


80 


442 


30 2 


1 1 I 


'° 3 


22 2 


2 9 


1024 


24 


42 


.6 


40 


22000 


100 


398 


100 


454 


100 


510 


28 8 


12 


" 3 


20 8 


2 I I 


0948 


24 


48 


16 


40 


24000 


90 


408 


90 


468 


90 


527 


30 8 


12 


" 3 


22 8 


2 n 


10S4 


24 


54 


16 


44 


26000 


80 


410 


80 


468 


80 


526 


32 8 


12 


" 3 


24 8 


2 It 


1219 


26 


48 


16 


44 


30000 


90 


4S0 


90 


548 


90 


6,7 






21 5 


2 9 


1272 


26 


54 


iS 


46 


32000 


80 


4S0 


80 


549 


80 


61S 






23 5 


2 9 


1431 


26 


60 


18 


48 


34000 


75 


501 


75 


572 


75 


644 






25 5 


2 9 


1 591 


28 


48 


18 


48 


32000 


90 


563 


90 


645 


90 


726 






21 9 


2 10 


1477 


28 


54 


iS 


52 


34000 


80 


563 


So 


645 


So 


727 






23 9 


2 10 


1662 


28 


60 


iS 


54 


36000 


75 


5S7 


75 


672 


75 


757 






25 9 


2 10 


1846 


3° 


48 


18 


56 


34000 


90 


646 


90 


739 


90 


833 






22 2 


2 10 


1694 


30 


54 


18 


60 


38000 


80 


6^6 


80 


740 


80 


834 


Shafts as de 


sired 


24 2 


2 10 


1906 


30 


60 


18 


64 


4OOGO 


75 


671 


75 


771 


75 


86S 






26 2 


2 10 


2118 


32 


48 


18 


58 


36000 


90 


736 


90 


841 


90 


948 






22 7 


2 10 


1928 


32 


54 


20 


62 


39000 


So 


734 


So 


841 


80 


947 






24 7 


2 10 


2166 


32 


60 


20 


66 


43000 


75 


766 


75 


877 


75 


9S8 






26 7 


2 10 


2410 


34 


54 


20 


78 


60000 


So 


840 


80 


961 


So 


1083 






24 1 1 


2 I I 


2477 


34 


60 


20 


78 


60000 


75 


865 


75 


99° 


75 


1115 






26 II 


2 II 


2720 



Horse-power. — In the computation of the power of an engine, the prime factors are area of cylinder, pressure of steam, piston speed, and point at which 
steam- is cut off. Our calculations of horse-power, as indicated in the above table, are based upon an initial steam pressure of 80, go and 100 pounds per square 
inch', valve gear cutting off at ^ stroke, piston speed varying from 500 feet for the smallest uj) to 750 for the largest size. These conditions can be changed, and 
by increasing one or all, the power of an engine is increased in like proportion. 



50 NOTES ON POWER PLANT DESIGN 



CONDENSERS AND ACCESSORIES 

The pressure in a condenser is always higher than the pressure due to the temperature of the 
steam. The difference between the pressure in the condenser and the pressure due to the tem- 
perature of the steam, gives the pressure exerted by the air in the condenser. The air comes 
in part from the feed water entering the boiler, in part from the circulating water, in the case of 
the jet condensers, and in part from leakages of air into the condensing outfit. Water at atmo- 
spheric conditions, contains from 2 to 5 per cent of air by volume. It is evident that the leakage 
of air into the condensers may be much or little according to the care with which the condenser outfit 
was installed. 

In general, a wet air pump handling the air and circulating water for a jet condenser, when 
running at a piston speed of 50 feet per minute, should displace in one hour from three to three 
and one-half times the volume of circulating water used per hour. The wet pump for a surface 
condenser handling both condensed steam and air, should displace per hour, 35 times the volume 
of water coming out of the condenser per hour as condensate. The displacement of 35 volumes 
is generally considered about right for a vacuum of 28 inches. If higher vacuua are carried, the 
figure should be increased, running up to perhaps 40. 

The vacuum in a condenser is generally measured either by the difference in level of mercury 
in a U-tube, or by the height of a column of mercury in a single tube, this height being measured 
above the surface in an open vessel filled with mercury, into which the tube extends. The differ- 
ence in level thus read, should be corrected for temperature, if the percentage of the perfect vacuum 
is to be obtained by comparison with a barometric reading reduced to 32 degrees and to sea 
level. This correction may be made with sufficient accuracy as follows: — 

The corrected height = observed height (1 - .0001 (t - 32) ). 

The amount of cooling water required for the condensation of a pound of steam is commonly 
figured, assuming a 20 degree increase in temperature with cold cooling water at 70 degrees. 
The heat to be abstracted from each pound of steam which has passed from the throttle through 
the condenser may be found by subtracting from the heat brought in by a pound of boiler steam, 
the heat transformed into work by a pound of this steam and the heat of the liquid condensate 
leaving the condenser. 

If steam is bled from or supplied to any stages or receivers of a turbine or engine, the amount 
of heat to be abstracted by the condenser may be calculated by the same process. Proper allow- 
ance of course must be made for the steam which is taken out before reaching the condenser and 
for the heat in any steam put back into the condenser and for the heat, from such steam, which is 
transformed into work. See in this connection the discussion of the bleeder type turbine under 
the general heading of Cylinder Efficiency and Rankine EflBciency. 



SURFACE CONDENSERS 

(1) The rate of heat transmission through a tube is nearly directly proportional to the mean 
difference in temperature between the liquid on the inside and the vapor on the outside of the 
tube. 

(2) The rate of heat transmission is proportional to the square root of the velocity of the vapor 
normal to the line of tubes. 

(3) The rate of heat transmission is proportional to the cube root of the velocity of the water 
in the tubes. 

An article by Mr. Orrok in "Power" of August 11, 1908, gives a summary of the various tests 
made on the transmission of heat through condenser tubes, A smooth curve representing the mean 
of the various experimental results was drawn by Mr. Orrok, who proposed the following formula 



NOTES ON POWER PLANT DESIGN 51 

for U the heat transmission per sq. tt. per hour per degree difference of temperature inside and 

outside of the tube: — _ 3 

f/ = 17 Ws V.023 + Vy, 

Vs = velocity of steam by the tube generally taken as 625 ft. p. sec. 
Vw = velocity of water in tube in ft. per sec. 

Values read from the curve give — 



3l. of water in tubes 
in ft. per second. 


U 


.5 
1 
2 
3 


350 
430 
545 
620 



Vel. of water in tubes 




in ft. per second. 


U 


4 


675 


5 


725 


6 


775 


7 


815 



Experiments by Mr. E. Josse have shown much higher values for tubes which were drained 
in such a way that the steam condensed on the upper rows did not trickle down over the lower rows 
but was drained to the shell, thus keeping the efficiency of the lower tubes equal to that of the upper 
tubes. For such tubes it appeared that the constant 17 in the preceding formula for U should 
be made 20 or 25. 

Later on Mr. Crrok did a considerable amount of experimental work on this subject and as 
a result of his more recent work he developed the following formula and conclusions which are 
copied from Transactions A. S. M. E., 1910. 

(a) The heat transferred from condensing steam surrounding a metallic tube to cold water 
flowing through the tube is proportional to the seven-eighths power of the mean temperature dif- 
ference of the water and steam temperatures. This is equivalent to the statement that the co- 
efficient of heat transfer, U, is inversely proportional to the eighth root of the mean temperature 
difference. 

(b) The coefficient of heat transmission, U, is approximately proportional to the square 
root of the velocity of the cooling water. 

(c) The coefficient U is independent of the vacuum and of the velocity of the steam among 
the tubes or in the condenser passages. It may be proportional to the square root of the velocity 
normal to the tubes, but in all common cases this velocity does not vary more than a tenth part. 

(d) The effect of air on the heat transferred is very marked indeed, particularly at high vacuua, 
and most of this air is due to leakage through the walls and joints of the apparatus. The effect 
of the presence of air in reducing the value of U is as follows: 

where Ps is the partial pressure due to the steam and Pt is the total steam and air pressure. 

(e) Taking the heat transfer of the copper tube as 1.00 under similar conditions the transfer 
for other materials is approximately as follows: — copper, 1.00, Admirality 0.93, aluminum lined 
0.97, Admiralty oxidized (black) 0.92, aluminum-bronze 0.87, cupro-nickel 0.80, tin 0.79, Admiralty 
lead-lined 0.79, zinc 0.75, Monel metal 0.74, Shelby steel 0.63, old Admiralty (badly corroded) 
0.55, Admiralty vulcanized inside 0.47, glass 0.25, Admiralty vulcanized both sides 0.17. This 
coefficient (due to the material of the tube) will be designated by n. Corrosion, oxidation, vul- 
canizing, pitting, etc., have also a marked effect in reducing the transfer. This reduction, best 
shown by the Admiralty tube which gave fx = 0.55, may reduce the transfer at least 60 per cent. 

(f) The foregoing conclusions may be expressed mathematically as follows: 



05 



52 NOTES ON POWER PLANT DESIGN 

where C = the cleanliness coefficient varying from 1.00 to 0.5 
fj, = material coefficient varying from 1.00 to 0.17 

(f = the steam richness ratio „ ^ varying from 1.00 to 

Vv, = the water velocity in ft. per sec. 
9 = the mean temperature difference. 
K = a constant, probably about 630. 

The effect of the length of tube, or rather length of water travel, has not been considered and the 
design of the condenser must be such that there is a free steam passage to every tube. 

(g) This expression for U is cumbersome to use and for modern turbine condenser work cer- 
tain conditions may be taken as well settled. The guaranteed vacuum i,, usually 28 ins. The 
entrance circulating water is usually 70 deg. and a 20-deg. temperature rise is considered economical. 
Under these conditions 6 =18.3 and 6'^ = 1.44. 6 calculated on the geometrical curve is 18.2. 
For these cases it will be nearly as accurate and much simpler to calculate 6 by the logarithmic 

no r\ 

method, neglecting 6 in the denominator and using 435 or :j— 77- for K^. The expression will then be 

U = K'C <p^ fM VV^ 

(h) The above equation agrees well with the results of a number of tests on full sized condensers 
under varying conditions. There appears to' have been no attempt to determine the amount of 
air handled by the air pump in these cases, but the amounts of air indicated by the formula are 
such as agree with the pressures and temperatures taken. 

Later work by Mr. Orrok, led him to suggest that the term ,^2 = / _£ j be substituted for tp^ in 

the expression for U. 

Tlae value 525 has been commonly used as the B. T. U. per sq. ft. per hour per degree difference 
in temperature. 

The modern surface condenser used for steam turbine work is designed t j maintain a tempera- 
ture in the hot well as near as possible to the temperature corresponding to the vacuum. 

The mean temperature difference is often taken as ts — — ^-^ where 4 = the temperature of 

the steam; th = the temperature of the hot condensing water and tc the temperature of the cold 
condensing water. 

The true mean temperature difference 6 = ^ ~ " 

, ts — h 

If < = any momentary temperature; W the weight of injection water per hour; Fthe B. T. U. per 
hour per square foot of surface per degree difference in temperature, and A the condensing sur- 
face in square feet. 

UdA{ts-Q = Wdt , ^f'^dt W, t.-h 

A =—J — = 77 loge -. 7- 



U tf^ts — ta U ts — t, 



eUA = With-tc) whence 6 = r — r 

ts — th 
• loge -J—T 



NOTES ON POWER PLANT DESIGN 53 

Illustration of method of calculating surface needed in a condenser. Condenser to handle 
15,000 lbs. steam per hour, the steam containing 6 per cent of moisture: Vacuun 28"; Barometer 
30"; cold water 70°; hot water 90°; condensate 5 degrees below temperature of steam. The dif- 
ference between the pressure in the condenser and that corresponding to the temperature of the 
steam is W of mercury in this case. Velocity of injection water through tubes 7 feet per second. 

Required total surface 30 — 28 — 25 

JJ = 435 X C X <p2 X yu ^Vw) using .75 for C and ^^r '— = .875 for 

<p\ .7 for li this becomes 435 x .75 x .76 x .7 x 2.64 = 458. 6 = 18.3 see item (g) in quotation 
from Orrok's paper. 458 x 18.3 = 8391. B. T. U. per hour per square foot of surface. 

The heat to be abstracted is 15000 (.94 r + q- 59.8) = 13,843,500 B. T. U.;t and q being taken 
at 1.75 X .491 = .86 lbs. absolute. 13,843,500 - 8,391 = 1650 square feet, the surface needed. 

In general from 1.2 to 2.5 square feet of surface are allowed per K. W. for large units, the 
amount of surface increasing to 4 square feet per K. W. for small units. 

WESTINGHOUSE-LEBLANC SURFACE CONDENSERS 

An Abstract from the May, 1914, Bulletin of the Westinghouse Machine Company. 

The principles governing the design of jet condensers, in which there is an intimate mixture 
of the steam and circulating water, are simple and well known, but in surface condensers where 
the heat of the exhaust steam is transmitted to the cooling water through metal tubes, the problem 
is more complex. 

In designing a surface condenser, the amount of steam to be condensed, the vacuum desired 
and the temperature and amount of circulating water available, are determinate. Not only do 
these bear a close inter-relation, but they have a marked effect on the other details of design. 

Knowing the total number of heat units to be taken from the steam and the amount of heat 
(depending upon its temperature rise) which each pound of circulating water will absorb, the 
amount of surface necessary to transmit the heat may be determined. This calculation will involve 
a consideration of the following: (1) The velocity of the circulating vvater, (2) the material used 
for tubes and their arrangement, (3) the mean temperature difference between the steam and water, 
and (4) the amount of air on the steam side of the tubes. 

(1) Careful investigations show that the heat transfer varies approximately as the square 
root of the velocity of the cooling water in the condenser tubes. Therefore, the higher the velocity 
of the water, the greater the heat transfer, but due account must be taken of the greater power 
required for high velocities. In general, the velocity should be such as will result in tumultous 
rather than smooth and stratified flow, thereby bringing each particle of water into contact with 
the surface of the tubes. 

(2) Different materials may be used for the tubes depending on the nature of the circulating 
water. Copper alloys are more generally used than other materiaL\ In the arrangement of the 
tubes, it is quite important that restricted passages be avoided so the steam may pass freely from 
one side of the condenser to the other, thereby avoiding undue pressure drop or loss in vacuum. 

(3) The amount of heat which will pass through the tube wall is proportional to the mean 
temperature difference which is determined by the expression — 

th — tc 



ts - th 
Loge f _ . 

when ts is the temperature of the steam, tc and th are the temperaturjes of the intake and discharge 
water respectively. For ordinary conditions, it is sufficiently accurate to use the arithmetical 
mean as calculated from the expression — 

, th + tc 

ts K~~ 



54 



NOTES ON POWER PLANT DESIGN 



(4) The most important factor affecting heat transfer is the presence of air on the steam 
side of the tubes. Some of this air is carried into the condenser with the ?team but this quantity 
is so small as to be almost negligible. The greater portion enters by leakage at valves and joints 
and by infiltration through the cast iron connections and the condenser shell. 

Under the low pressure conditions existing in a condenser the density of air is greater than 
steam. So if any appreciable amount of air is present it will collect in the bottom of the condenser 
and "dro^vn" or "blanket" the lower tubes, thereby preventing the steam from coming into proper 
contact with them. It is therefore necessars", if the best results are to be obtained, that the air 
be removed continuously and completely from the steam space. 

Any air in the steam space will have a finite pressure and the total pressure would be due partly 
to steam and partly to air pressure. As may be seen by reference to any "Steam Tables" the vapor 
at a given pressure has a definite temperature — the lower the pressure, the lower the temperature. 
It is obvious that if the air pressure is high, the steam pressure is low with a correspondingly low 
temperature. 

A concrete case in tabular form will make this relationship clear. In some condensers the 
difference in temperature between the upper and lower portions of the steam space may be 10 
or 15° F., while in others not more than 1 or 2° F. Assuming the total absolute pressure in the 
top of the condenser to be 0.975 pounds per square inch, (vacuum 28.01") and temperatures of 
85, 90 95, and 100° F. in the lower portion of the steam space with no pressure drop in passing 
through the condenser, the resulting air and steam pressures are as follows: 



Temperatures in bottom of Condenser 

Total pressure lbs. per square inch 

Steam pressure corresponding to assumed temperature 

Air pressure 



85° 
0.975 
0.594 



90° 
0.975 
0.696 



95° 
0.975 
0.813 



100° 

0.975 

0.946 



0.381 0.279 0.162 0.029 



From this tabulation it will be seen that with a vacuum of 28.01" if the air pressure is 0.381 
the maximum temperature of the steam in the lower portion of the condenser is 85° F., when 0.279 





Cross-section showing arrangement of Tubes 



pounds 90° F., etc., showing very clearly how the pressure of air lowers the steam temperature 
and consequently, the "heat head" between the steam and cooling water. It is only by remov- 
ing the air to the lowest possible amount, that the maximum "heat head" and consequent rate of 
heat transfer may be secured. 

Another loss arising from the presence of air is due to the fact that the temperature of the con- 
densate must be raised a greater amount the higher the air pressure. 

The condenser shell which is usually circular in form, is made of exceedingly close grained cast 
rion, the location of the water and steam connections being determined by local conditions. 



NOTES ON POWER PLANT DESIGN 



55 



In the smaller sizes, say up to 10,000 square feet, the shell and nest of tubes are concentric, 
as shown at the left in the cross section on the page preceeding this. 

The pitch and arrangement of the tubes is such that the pressure drop of the steam in passing 
from one side to the other is negligible. 

In large condensers, owing to the distance the steam has to travel, special care is necessary 
to prevent undue resistance and consequent loss in vacuum. At the right in this same cut is a 
sectional view of a large condenser. The nest of tubes is placed non-concentric to the condenser 
shell, so that steam enters around the whole periphery. Such an arrangement practically doubles 
the area for the admission of the steam, and so results in a velocity only one half of that in other 
types. The air offtake consists of two parallel plates extending the entire length of the condenser, 
thus reducingthe distance the air has to travel to one half of that in the older types of condensers. 

As all condensate must fall through the surrounding envelope of live steam, its temperature 
will be practically the same as that of the entering steam. 

The advantages of this arrangement may be summarized as follows: 

First: Non-concentric arrangement of tubes gives a steam velocity only one half of that in 
the ordinary type. 

Second: Radial flow reduces the length of the steam path through the tubes to one half of 
that ordinarily existing. 

Third: Highest possible temperature of condensate. 

How well this design fulfills its purpose, is shown by numerous tests made on large condensers 
where the temperature of the condensate was found to be within one or two degrees of that of the 
incoming steam, and the difference in pressure between the air pump offtake and the top of the 
condenser not more than 0.1" mercury. 

The condenser tubes used are of different standard materials depending on the character of 
the cooling water. Muntz metal is generally used for both the tubes and tube sheets. To pre- 
vent sagging, long tubes are supported between the ends, the number of supports depending on 
the length. The method of packing each end of the tubes is shown by the cut. 
C is a fibre packing held in place and expanded by bronze nut D. The 
fibre expands when wet and makes a tight joint which is, however, easily 
removable in case it is necessary to replace a tube. 

In view of the importance of completely scavenging the condenser 
of air, it is obvious that the air pump must be capable of handling it 
at extremely low pressures from which it must be compressed to that 
of the atmosphere. The fact that the volumetric efficiency of the West- 
inghouse-Leblanc Air Pump increases as the density of the air which it 
is handling decreases, gives it a singular suitability for such service. 

The ideal air pump would be one in which the volumetric efficiency 
increased at such a rate that constant weight of air would be handled. 
While this is clearly impossible, careful tests show that the Westihghouse- 
Leblanc pump more nearly approaches the ideal than any other. Its -Tube packing 

volumetric efficiency increases rapidly, even after the reciprocating pump (due to limitations of 
clearance) has' ceased to be of any value whatever. 

The mechanical simplicity and ruggedness of the air pump makes it an ideal adjunct to the 
surface condenser. The only moving part of the pump is the rotor or impeller, marked J, which 
is a solid bronze casting practically indestructible under ordinary water conditions. 

By referring to the figure on page 57 which shows an air and condensate pump mounted on the 
same shaft, it will be seen that air enters the^pump through the pipe C. To start the pump in oper- 
ation, high pressure steam is turned into the connection D. The cone forms the annular nozzle 
of a steam ejector, so that on opening the valve in the steam line a vacuum is created in the body 
of the air pump. The chamber E being piped up to a source of water supply, is immediately filled 
on account of the vacuum created by the steam ejector. Water then flows through the distributing 
nozzle F and is projected in layers through the combining passage G into the diffuser H. Between 
the successive layers of water, layers of air are imprisoned, these layers of water (on account of the 
high peripheral speed of the turbine wheel which throws them off) have a velocity sufficient to 
enable them to overcome the pressure of the atmosphere and force their way out of the pump in 




56 



NOTES ON POWER PLANT DESIGN 




TURBINE 



Cross-Section of Air and Condensate Pump 

which a high vacuum exists. The layers of water act like a succession of w^ater pistons with large 
volumes of air between them. 

Cold water is used in the air pump; the specific heat of air is low and its weight small com- 
pared with that of the water, and there- 
fore the air is immediately cooled on 
entering the pump to the lowest possible 
temperature. 

The water discharged from the air 
pump is not appreciably heated, and may 
therefore, be returned to the cold well. 
It must be remembered, however, that in 
reality a mixture of water and air is dis- 
charged, so that in discharging to the cold 
well, proper provision must be made for 
separating the air from the water. 

The advantage of such a pump may 
easily be seen. There are no close clear- 
ances or rubbing surfaces requiring con- 
stant attention — no reciprocating parts 
with their attendant packing troubles. 

It is obvious that the air handling 
capacity of this pump, owing to the use 
of water pistons, is much greater than the 
ordinary ejector arrangement where the 
air is simply carried along by friction. It 
is to be noticed that the water is dis- 
charged through a . comparatively large 
opening through which small debris may 
pass without danger of clogging. Some 
hydraulic pumps of this general type, have 
a very narrow discharge opening extend- 
ing around the entire circumference, and 
as a result much trouble is experienced 
from foreign matter, and it is often nec- 
essary to use perfectly clean water co 
insure satisfactory operation. 

The pump that takes the condensed 
steam from the condenser is usually called 
the condensate pump. Although it is in 

-Typical Surface Condenser Installation pOUlt of slze, probably the SmallcSt of 




NOTES ON POWER PLANT DESIGN 57 

the condenser appurtenances, its function is just as important as that of the others. It draws 
the water from the high vacuum within the condenser and discharges it to the desired place, — 
usually the feed water tank. 

This pump is of the single stage centrifugal type, usually driven by its own turbine. If desired, 
the condensate pump may be placed on the end of the air pump shaft. 

The accompanying cut shows how readily the larger condensers may be placed directly beneath 
the turbine. In this particular case, the condensate and air pump are mounted on one shaft 
which is turbine driven. The circulating pump is also turbine driven. 

The condensers described, have been developed for the production of high vacuua and are 
intended primarily for use with steam turbines where such vacuua may be effectively utilized. 

They have been built in sizes ranging from one thousand to fifty thousand square feet in a single 
shell, the latter probably being the largest ever constructed. 



CONDENSER TESTS 

The following extracts from tests made on Westinghouse Surface Condensers after installation 
show in a striking manner how completely the air is removed from the steam space, and how closely 
the temperature of the condensate corresponds to that of the steam entering the condenser. 

PUBLIC SERVICE ELECTRIC CO. Size — 20,000 Sq. Ft. 

Marion, N. J. Connected to 9,000 K. W. 

_ High Pressure Turbine. 

Date, Oct. 26th, 1913. 3 P. M. 4 P. M. 

Load in K. W. on Turbine , 9,000 6,000 

Barometer 30.16 30.14 

Vacuum at top of Condenser by Mercury Column 28.96 29.05 

Temperature at Top of Condenser °F 83 79 

Temperature Condensate Pump Water °F 82 79 

Vacuum at Air Pipe Connection 29 . 08 29 . 12 

Temperature Injection Water Inlet °F 66 . 5 68 

Temperature Injection Water Discharge °F 78 76 

CAMBRIDGE ELECTRIC LIGHT CO. Size — 5,000 Sq. Ft. 

Cambridge, Mass. Connected to 1,500 K. W. 

Low Pressure Turbine. 

Date, May 28th, 1913. 9 A. M. 11 A. M. 1 P. Ml 

Load in K. W. on Turbine 1,225 1,275 1,250 

Barometer 29.88 29.88 29.88 

Vacuum at Top of Condenser by Mercury Column 28.56 28.55 28.55 

Temperature at Top of Condenser °F 84 85.5 85 

Temperature Condensate Pump Water °F 82 82.5 82.5 

Vacuum at Air Pipe Connection 28.7 28.66 28.65 

Temperature Injection Water, Inlet °F 59 59 59 

Temperature Injection Water, Discharge °F 77 77^ 77 

DETROIT UNITED RAILWAYS CO. Size — 4,000 Sq. Ft. 

• Monroe, Michigan. • Connected to 2,000 K. W. 

High Pressure Turbine. 
Date, August 10th, 1913. 9 A.M. 9.30 A.M. lOA.M 

Load in K. W. on Turbine 2100 1800 2100 

Barometer 29.25 29.25 29.25 

Vacuum at Top of Condenser by Mercury Column 27 . 20 27 . 25 27 . 20 

Temperature at Top of Condenser °F .102 102 103 

Temperature Condensate Pump Water °F 100 100 101 

Vacuum at Air Pipe Connection 27,20 27 25 27.25 

Temperature Injection Water Inlet °F 84 84 84 

Temperature Injection Water Discharge 101 100 101 



58 



NOTES ON POWER PLANT DESIGN 

Air PufTtp Di^ch. 

Y 




C/rc. lYarer Inlef- 






Area stf H: 


/OOO 


200 O 


3000 


■4-000 


sooo 


Condensate dio 


3' 


3' 


4-' 


3" 


3' 


A 


l9'-0g 


19'-/ O,^ 


26'-3f 


27'-o" 


27'-sf 


d 


9'-6f 


9'-4k' 


I2'-I0k' 


12- ek" 


'2-4/ 


B 


is'-9f 


je'-Bji 


20'-9M' 


20'- 7^' 


2l'-OJ§' 


* e 


9" 


9" 


7' 


13 


13" 


C 


s'-af 


3'-2s 


3'-2f 


4-'-li" 


4-'- 14:" 


f 


6£ 


6/ 


9" 


lOk' 


lOk' 


D 






^'-^i' 


^-^i' 


^•-3^' 


Air Pump dia 


3" 


3f 


6' 


6' 


6" 


E 


e'-/o£ 


7'-<' 


5-7.1" 


9'-9X 


9'-^li' 


9 


3--0f 


3'-0f 


3-2' 


3-2f 


3'-2f 


F 


2'-7^" 


3-7^ 


3'-//^" 


^■-6^' 


S'-l^" 


* h 


2-4-' 


2 -8 k' 


4-'-3k" 


3'-ll^' 


4'-lf 


* G 


^'-^/ 


2 -8b 




3'-7f 


3'- Ilk" 


k 




^r 


6' 


s' 


s" 


H 






^i" 


ei" 


^i" 


Priming td/a. 


'¥ 


2" 


z" 


2 


s' 


J 


^'-9E 


S'-S^" 


6'-sf 


6 '-8^' 


7-3^" 


* m 


I3f 


'^i' 


22" 


20k 


20k' 


K 


/7/ 


'7i" 


'dg 


ao£ 


20^' 


<i> n 


3g 


3k' 


/2f 


llf 


llf 


L 


^4' 


2'-9§" 


B'-yf 


3'-3i" 


2''9f 


Cirv. Inlet dia 


7' 


12' 


14' 


/(>' 


18" 


M 


6" 


/o" 


/o' 


/4" 


I4-' 


P 


'^'-li' 


^■-7f 


4-'-il" 


4'-llf 


S'-3k" 


N 


8' -3" 


I'-o" 


II -2" 


8' -10" 


lo'-o" 


9 


le" 


18' 


a'-a' 


2'-e>" 


2'- 4' 


O 


a'- 6" 


J '-4-" 


3-9" 


4-'-8" 


4- '-10" 


C/'rc. Disch. dia. 


7" 


12" 


14' 


16' 


18" 


P 


/a' 


23" 


2'- 4-" 


-? '- 7 " 


2'- 10" 


r 


/a" 


IS' 


18" 


19" 


21" 


Q 


I2£ 


,2k' 


llf 


/^i' 


I9M 


Turb. 3t d/a 


2s 


2k" 


2k' 


2k' 


2k' 


/? 


18' 


18' 


4'-er' 


^'-",7" 


4'-ll,f 


t 


izi" 


12k' 


'2s 


lof 


'Of 


s 


2'-l" 


2-7" 


2'-7f 


2'-ll^" 


2'-iir 


u 


isf 


isf 


isf 


19" 


/9' 


■St. /e/ef c^/a 


2Z' 


36' 


4-2" 


4-a' 


4-8" 


\r ■ 


^£ 


■^k' 


4k' 


37Z 


3^" 


a 


6-uf 


7-/5-" 


9 '-of 


a'-iof 


8- llf 


Turb- S'X- d/a. 


4' 


4' 


4-" 


6' 


6' 


b 


2j£ 


/-7i' 


2-8" 


3-0" 


3-3" 


»^ 


iH' 


17k' 


17k' 


'7rl' 


''16 














y 


n" 


11' 


11" 


Ilk" 


Ilk" 



Note:- 

In the 1000 ana/ 2000 j^. ft, s/zss no rectucing gear is ussid, 
the turbine couples direct to pump ^. 

^ Where no reducing gear is used these connections are on 
other side of cona/enser from thaf st)o^vn in c/iogrom. 

(j> In th^o smallest -sizes priming connect/on opens alon/ntyard. 



NOTES ON POWER PLANT DESIGN 

THE WHEELER CONDENSER AND ENGINEERING COMPANY 
WHEELER ADMIRALTY SURFACE CONDENSER 





Sq. Ft. 














Diameter 




of 














of 


Weight 


Surface 


A 


B 


C 


D 


E 


F 


Tube 


Lbs. 


463 


7'-0" 


8'-3" 


3'-0" 


15J<" 


21 J<" 


18H" 


Vs" 


3400 


606 


8'-0" 


9'-4" 


3'-l" 


16X" 


22><" 


22H" 


Vs" 


4500 


751 


8'-0" 


9'-7" 


3'-0" 


IQVs" 


22><" 


2'-l" 


Vs" 


5200 


1042 


8'-0" 


9'-8" 


3'-5" 


18K" 


2'-2j^" 


2'-3K" 


Vs" 


6600 


1109 


8'-0" 


9'-5" 


3'-8" 


IQVs" 


2'-2K8" 


2'-4><" 


y." 


7200 


1379 


8'-0" 


lO'-O' ■ 


4'-0" 


221/8" 


2'-5^" 


2'-9^" 


y," 


9200 


1778 


8'-0" 


10'-2" 


4'-4" 


23'A" 


2'-8X" 


3-2" 


y" 


11100 


2051 


8'-0" 


10'-2" 


4'-8" 


2'-l" 


2'-ll>^" 


3'-4" 


y" 


12900 


2223 


lO'-O" 


12'-5" 


4'-6" 


2'-l" 


■ 2'-8>^" 


3'-2" 


y" 


14000 


2757 


8'-0" 


10'-8" 


5'-4" 


2'-3X" 


2'-93^" 


3'-10" 


y" 


16200 


3446 


lO'-O" 


12'-7" 


5'-4" 


2'-5>^" 


3'-lK" 


3'-10" 


y" 


19600 


4135 


12'-0" 


14'-7" 


5'-4" 


2'-5>^" 


3'-l>^" 


3'-10" 


y" 


23000 


4679 


12'-0" 


15'-0" 


5'-6" 


2-6" 


3'-4>^" 


4'.y," 


y" 


26500 


5069 


13'-0" 


16'-0" 


5'-6" 


2'-6" 


3'-4>^" 


4'->^" 


y" 


28300 


5849 


• 15'-0" 


18'-0" 


5'-6" 


2'-6" 


3'-4>^" 


i'.y," 


y" 


31800 


6733 


15'-0" 


17' 0" 


5'-8" 


2'-7" 


3'-7>^" 


4'-6" 


y" 


36900 


7714 


13'-0" 


16'-0" 


6'-6" 


3'-0" 


4'-2>^" 


5'-2K" 


y" 


44200 


8307 


14'-0" 


17'-0" 


6'-6" 


3'-0" 


4'-2K" 


5'-2K" 


y" 


46700 



60 



NOTES ON POWER PLANT DESIGN 



WESTINGHOUSE LE BLANC JET CONDENSERS 

SIZES 




































Dia. 


Dpenings 


8zb 


1 


2 


4 


5 


6 


7 


8 


9 


10 


11 


12 


13 


14 


15 


16 


17 18 


19 


20 


21 


1 


3"-4y2 


6"-6 3/4 


30 


333/8 


261/2 


163/4 


151/8 


10 


91/7 


25 V: 


22 34 


35 Vs 


2, 


6"-ll/4 


13% 


22 5 


3 


6 


5 


2 


3 "-4 1/2 


6 "-6 3/4 


31 y 


333/s 


261/2 


163/4 


151/8 


10 


91/, 


25% 


223/g 


35 ys 


2 


6"-li/4 


13% 


22 5 


3 


6 


5 


4 


3"-10V2 


7"-iy8 


33 


34 


273/4 


18 


151/, 


10 


91/, 


253/ 


23% 


3 "-2% 


28% 


6"-6y8 


141/4 


28 6 


3% 


7 


5 


5 


3"-10y2 


7"-l% 


351/6 


34 


273/4 


18 


151/, 


10 


91/, 


253/4 


23 Vr 


3 "-2% 


28% 


6"-6y8 


141/4 


28 6 


4 


7 


5 


7 


4"-4V2 


8"-5i/2 


3 "-3 


35 H 


271/8 


20 


173/, 


10 


10 y, 


301/4 


25 


3"-5% 


313/, 


7"-10 


151/4 


30 7 


4 


Cl 


6 


8 


4 "-4 1/2 


8"-5i/2 


3"-7 


35 H 


271/8 


20 


173/4 


10 


10 1/, 


301/4 


25 


3"-5y 


313/t 


7"-10 


151/4 


30 7 


S 


V 





10 


5"-0 


8 "-8 1/4 


3"-10i/2 


35i| 


271/8 


20 


18% 


10 


10 v, 


301/4 


251/4 


3"-9% 


35 


7"-103/4 


151/4 


36 9 


6 


12 


G 


U 


5"-0 


8"-8i/4 


4"-0i/2 


35 M 


271/8 


20 


181/8 


10 


10% 


301/4 


251/4 


3"-9% 


35 


7"-103/, 


15% 


36 9 


6 


n 


6 


13 


5"-7i/2 


9"-10y8 


4 "-8 


3"-7y8 


34 y8 


21 


19 


10 


113/ 


353/4 


28% 


4"-13/f 


3"-3 


8"-ll% 


20% 


42 12 


6 


14 





U 


5 "-7 1/2 


9"-ioy8 


5"-0 


3"-7y8 


34 ys 


21 


19 


10 


113/1 


353/4 


28% 


4"-13/8 


3 "-3 


8"-l 1 % 


20% 


42 12 


7 


14 


6 


16 


0"-7i/2 


10"-113/8 


5 "-6 34 


3"-10H 


3"-lA 


24 


193/4 


9% 


14 


3"-7 


29 y. 


4 "-8 1/2 


3"-7i/, 


9"-113/8 


22% 


48 14 


8 


If 


10 


17 


6"-7i/2 


10"-113/8 


6"-0 


3"-10|i, 


3"-lA 


24 


193/4 


9% 


14 


3 "-7 


29% 


4"-8i/2 


3"-7% 


9"-113/8 


22% 


48 14 


9 


10 


10 


18 


7 "-5 1/2 


13"-5i/2 


6 "-4 1/2 


4"-6H 


3"-8A 


3"-10i/4 


18% 


9% 


14 


4"-3l/4 


291/2 


5"-li/2 


4"-2 


12"-2i/2 


293/4 


54 18 


9 


20 


10 


19 


7"-5i/2 


13"-5i/2 


6"-8i/2 


4"-6H 


3"-8A 


3"-10i/4 


18% 


9% 


14 - 


4"-3i/4 


291/2 


5"-li/2 


4"-2 


12"-2y2 


293/, 


54 18 


9 


20 


10 



NOTES ON POWER PLANT DESIGN 



Gl 



WESTINGHOUSE LEBLANC JET CONDENSERS 

CAPACITIES 

Turbine Driven 

Based on 5° Terminal Difference. 



Con- 


Circulating 




» 






28" VACUUM 










denser 


Wpt-r 






















Number 


Lbs.per Hr. 


35° F. 


40° r. 


45° F, 


50° F. 


50° F. 


■55° F. 


60° F. 


70° F. 


75° F. 


80° F. 


1 


235,000 


17200 


15750 


14400 


ISCOO 


11575 


10150 


8750 


7300 


5950 


4500 


2 


320,000 


20SC0 


19200 


174C0 


15700 


14000 


12250 


10500 


8800 


7200 


5450 


4 


350,000 


22750 


20750 


19000 


17100 


15880 


13400 


11600 


9550 


7800 


5950 


5 


400,000 


26000 


23800 


21700 


19600 


17500 


1.5325 


13200 


11050 


9025 


6820 


7 


000,000 


39000 


£5750 


32750 


290C0 


26400 


23000 


19750 


16600 


13400 


10250 


8 


750, ceo 


49000 


44750 


40750 


37000 


32750 


2rooo 


24800 


20500 


16750 


12850 


10 


825,000 


53500 


49000 


44750 


40400 


34750 


31800 


27300 


22750 


18400 


14100 


11 


940.000 


610C0 


55800 


51000 


46000 


41000 


36000 


31000 


25750 


21000 


16000 


13 


1,200, OCO 


775C0 


71000 


C5200 


58600 


52750 


46000 


39250 


33250 


26600 


20500 


14 


l,5.50,0CO 


100600 


92500 


84000 


75750 


57750 


59300 


51150 


42750 


34650 


26400 


16 


l,850,CfO 


120500 


11000 


100500 


910C0 


81000 


71000 


61000 


51000 


41500 


31600 


17 


2,200 OCO 


143000 


I310C0 


119000 


107500 


96000 


84000 


72500 


60800 


49250 


37500 


18 


2,620,000 


170000 


356000 


142000 


128000 


114500 


100320 


86300 


72250 


58600 


44500 


19 


3,000,000 


194700 


178500 


163000 


147000 


131000 


1150C0 


99040 


82000 


67000 


61100 


20 


4,000,000 


26C00O 


238000 


217500 


196000 


174600 


1.53200 


132000 


110300 


89400 


68100 


21 


5,000,000 


325CC0 


298000 


271500 


245000 


218500 


191500 


165300 


138000 


111600 


85200 


22 


6,000,000 


2S90CO 


S57C0O 


?25000 


293000 


262000 


2300C0 


198000 


166000 


134000 


102000 


23 


7,000 000 


4550C0 


416000 


£80000 


3420GO 


305000 


268000 


231000 


194000 


156000 


119000 


24 


9,000,000 


5800C0 


530C00 


485000 


447000 


390000 


344000 


295000 


248000 


212000 


153000 


25 


11,000,000 


710000 


65C0C0 


590000 


545000 


475000 


420000 


360000 


3O4000 


258000 


187000 


26 


13,000,000 


8400CO 


77C0C0 


700000 


645000 


560000 


495000 


425000 


360000 


305000 


220000 



The figures given aro based on the assumption that the temperature of the mixture of water and steam is 5 degrees 
less than the theoretical temperature corresponding to the vacuum. 
The following conditions are assumed: 

1. That condenser pumps are steam driven. 

2. Temperature of injection water . 70 Degress F. 

3. Level of watar supply bslow top of condenser dDss not exceed 13 Feet 

4. Discharge water is to be elevated above base of condenser, not to exceed (including 

pipe friction) 4 Feet 

5. Suction pipe is to be so arranged that friction head will not exceed the equivalent of. 2 Feet 

6. Vacuum at rated load, referred to a barometric pressure at 30 inches ... 28 Inches 



C2 



NOTES ON POWER PLANT DESIGN 



THE WHEELER CONDENSER AND ENGINEERING COMPANY 
DIMENSIONS OF WHEELER-EDWARDS AIR PUMP 






Capacity 


















in lbs. per 


















hour 
















Size 


28" Vac. 


Suction 


Discharge 


A 


B 


C 


D 


E 


3Kx8x6 ' 


22£0 


3" 


3" 


5'-2'^" 


2'-3" 


8%" 


16?^" 


22" 


4x10x8 


4500 


4" 


4" 


6'-7" 


2'-6" 


10^" 


20>^" 


2'-6" 


5x12x10 


7500 


5" 


5" 


7'-9" 


3'-0" 


13" 


243X" 


3'-0" 


6-14-10 


107£0 


6" 


6" 


8'-2" 


3'-6" 


15" 


2'-2K" 


3'-3" 


7-16-10 


14000 


6" 


6" 


8'-8" 


4'-0" 


^ I^Va" 


2'-2" 


3'-6" 


8-18-12 


20750 


7" 


7" 


9'-6" 


4'-6" 


18" 


2'-8" 


3'-9" 


8-20-12 


26000- 


8" 


8" 


9'-8" 


4'-6" 


, 18K" 


2'-8" 


3'-9" 


9-24-12 


36750 


10" 


10" 


9'-10" 


5'-0" 


21K" 


2'-my2" 


4'-4" 


10-26-12 


43250 


12" 


10" 


10'-8" 


5'-0" 


23H" 


3'-0" 


4'-4" 


12-30-14 


62500 

















NOTES ON POWER PLANT DESIGN 



63 



THE WHEELER CONDENSER AND ENGINEERING COMPANY 
DIMENSIONS OF WHEELER ROTATIVE DRY VACUUM PUMP 

H A H H E- 

I 




Capacities for 
Condenser Surface 

in lbs. per Size Size 

Size hr. 28 ' Vac. Suction Discharge A B C qD E 

5-12-12 18000 4" 2" 9'-ll>^" 3'-l" 3'-3" 17}4" 2'-l" 

7-14-14 27400 4>^" 3" 11' 3%" 3'-6" 3'-6" 20" 3'-4" 

7-16-10 34600 5" 3" 11 -3 J^" 3'-8" 3'-6" 22" 3'-4" 

9-18-16 48000 6" 4" 13-4" 4'-3" 4'-6" 24" 4'-l" 

9-22-16 68600 8" iH" 13'-5>^" 4'-7" 4'-6" 2'Aj4" 4'-l" 

10-26-18 102600 9" 5" 15'-53^" 5'-J<" 5'-6" 2'-S}4" 5'-0" 

12-30-18 130000 10" 6" 15'-7" 6-3^" 5'-6" 3'-4" 5'-0" 

14-34-18 154600 14' 6" 15'-6" 6'-4" 5'-6" 3'-5" 5'-3y<' 

16-30-24 160000 10" 6" ' 19'-9" 6'-7K" 7'-0" 3'-K" 5'-9" 

16-36-24 197000 16" 8" 20'-7K^" 6'-5" 7'-0" 2'-9>^" 5'-9" 

Note: — For 26" Vacuum capacity may be doubled. 
For 27" Vacuum capacity is 50% greater. 
For 283^" Vacuum capacity is 25% less. 




LONGITUDINAL SECTION OF AIR CYLINDER 

•=howing Rotative Valve and Flash Port for minimizing 
clearance less. 



WHEELER PATENT COMPOUND DISCHARGE 
VALVE 

The lift if regulated by outside adjusting screws; if water 
collects in the cylinder the secondary spring compresses 
and gives extra large lift. 





64 



NOTES ON POWER PLANT DESIGN 



THE WHEELER CONDENSER AND ENGINEERING COMPANY 
WHEELER DUPLEX HOT WELL PUMP 






Capacity 


















lbs. per 
















Size 


hour 


Suction 


Discharge 


A 


B 


C 


D 


E 


3x2^x3 


4200 


2" 


\y^" 


2VA" 


2'-iy,-' 


121^" 


wy 


5X" 


4j^x4x4 


11500 


2K" 


IW 


3'-63/8" 


3'-63/," 


17H" 


14" 


8^8" 


5Xx4><x5 


19000 


3" 


2K" 


3'-10X" 


3'-10K" 


18 54" 


16" 


9A" 


6x5^x6 


33500 


4" 


3" 


4'-0' 


4'-0" 


2'-l" 


22" 


14^" 


6x7>^x6 


57000 


6" 


5" 


4'-10" 


4'-10" 


2'-6K" 


2'-l>^" 


15" 


6x8>^x6 


73500 


6" 


5" 


4'-10" 


4'-10" 


2'-6X" 


2'-ly2" 


15" 


7>^x8KxlO 


98000 
















10x10x10 


142000 


8" 


7" 


&.y," 


6'-J<" 


3'-4>i" 


3'-6>^" 


7K" 


10x12x10 


195600 


10" 


8" 


6'-lK" 


6'-lK" 


2'-9>^" 


3'-ll" 


8><" 



NOTES ON POWER PLANT DESIGN 



65 



THE WHEELER CONDENSER AND ENGINEERING COMPANY 
WHEELER CENTRIFUGAL PUMP 



^iScAoiTfe 






Gallons per 














Size 


Minute 


A 


B 


C 


D 


E 


F 


4" 


400-475 


18^" 


12K" 


15^" 


9J<" 


17^" 


21K" 


5" 


600-725 


22" 


12>^" 


20J<" 


IVA" 


19^" 


23^" 


6" 


900-1050 


23" 


15" 


22>^" 


12" 


2VA" 


2'-l" 


8" 


1600-1900 


2'-3^" 


16" 


2l%" 


14K" 


2'-2" 


2'-53^" 


10" 


2500-3000 


2'-7" 


18" 


24^" 


16" 


2'-6X" 


2'.\VA'- 


12" 


3500-4200 


Z'-y^" 


22" 


2'-4>^" 


. 18K" 


2'-9" 


3'A" 


14" 


4800-5600 


3'-6" 


22" 


2'-6K" 


21J<" 


2'-6><" 


2'-llJ<" 


16" 


6400-7500 


3'-9" 


23>^" 


2'-8K" 


233-^" 


2'-9><" 


3'-2>^" 


18" 


8000-9500 


4'-l^" 


2'-l" 


3'-2" 


2'-0" 


3'-2?<" 


3'-ll>^" 


20" 


10000-11600 


4'-l" 


2'-3" 


2'-ll" 


22>^" 


3'-4>^" 


4'-K" 


SA" 


14000-17000 


4'-10K" 


2'-8" 


4'-0" 


2'-4" 


4'-0" 


4'-8" 


30" 


22000-26000 


5'-4" 


3'-3" 


3'-10" 


3'-2" 


5'-K" 


5'-7" 



66 



NOTES ON POWER PLANT DESIGN 



C. H. WHEELER SPECIAL EXHAUST GATE VALVE 




Size of 










DIMENSIONS 












Valve 
























A. 


B 


C 


D 


E 


F 


G 


H 


J 


K 


L 


M 


16 


8 


14 


16 


42 


48 


10 


23>^ 


IVs 


13>^ 


IVs 


16 


20 


10 


14 


20 


54 


53 


11^ 


271^ 


VA 


16 


IVs 


20 


24 


10 


16K 


24 


55 


59 


13 


32 


1^ 


16 


m 


20 


30 


14 


18 


30 


65 


69 


UVs 


38^ 


IK 


21 


w% 


24 


36 


18 


20 


33 


77 


83 


16 


46-^ 


IH 


25 


1V-, 


36 


42 


20 


22 


42 


89 


95 


16 


53X 


2 


27K 


V/2 


36 



C. H. WHEELER 



T" 



t1 



M ^ 



C. H. 



^ 



WHEELER C 




Surface Condenser with Multiflex Automatic Relief Valve, Gate Valve and Expansion Joint. 



NOTES ON POWER PLANT DESIGN 



67 



THE C. H. WHEELER "MULTIFLEX" PATENT EXHAUST RELIEF VALVE 

This valve consists of a brass valve deck which is indived into a number of rectangular port'^ 
arranged in rows, each port accurately faced on an angle and covered by a flap valve made of Phos- 
phor Bronze sheet, coiled at one end. The valves in each row are mounted on, and controlled by, 
a slotted bronze stem, to one end of which is keyed a bronze crank; these cranks have a common 
connecting rod which communicates with an external lever and locking device which not only 
allows the valves to be secured in either an open or closed position, but the valves can be seated 
with any desired degree of tension, because of the coiled spring. The angle of the ports and valve 
seats avoids abrupt turns and gives the steam an easy, smooth and noiseless passage through the 
valve. 

In normal operation the vacuum, or unbalanced condition of the atmosphere, holds the valve,* 
tightly on their seats; but to insure absolute tightness for high vacuum service, a water seal with 
brass globe valve on inlet side and visible funnel overflow with drain connection on discharge is 
provided. 





Size of 




Valve 




A 


B 


6 


28K 


8 


28K 


10 


29 


12 


29 


14 


37 


16 


42 


18 


37 


20 


45 


24 


56 


30 


64 





DIMENSIONS 


C 


D 


9^ 


11 


^'A 


13>^ 


13^ 


16 


15J^ 


19 


12 


21 


13 


23>^ 


21 


25 


19 K 


27K 


26 J^ 


32 


26 


38M 



E 


Shipping Weight 


IVh 


330 lbs 


li/s 


384 " 


m 


900 " 


Wa 


975 " 


m 


1128 " 


IH 


1440 " 


VA 


1995 " 


VA 


2440 " 


\A 


3822 " 


\y. 


6000 " 



68 



NOTES ON POWER PLANT DESIGN 



KNOWLES VERTICAL AUTOMATIC EXHAUST RELIEF VALVE 




With screw lifting device 



s 


D 


L 




H 


A 


B 


HH 


1, 


« 

i 


Number 




^ 














Si7,e 


V C 

B = 
.2 fc 
Q 


2 


Width 


Height 


Height 
above 
Gentle 


Distance 
below 
Centre 


Height 
Over All 


S 5 


S 5 

E 2 

S « 


and Size 
of Bolts 


4 


9 


12 


9 


lOlf 


cl 1 


54 


16A 


1 


74 


4-1 


5 


10 


134 


lU 


13 


64 


64 


m 


* 


«4 


8-f 


6 


11 


15 


12;^ 


14|t 


7S 


7tV 


21H 


i 


94 


8-f 


8 


13^ 


18 


17 


17^ 


9J 


84 


25 




111 


8-f 


10 


16 


24 


23 


231 


111 


lis 


31S 


14 


14J 


12—1 


12 


19 


26 


25 


27S 


144 


12i 


m 


1* 


17 


12—1 


14 


21 


32 


29 


318 


16S 


15 


43 


n 


181 


12-S 


16 


23^ 


36 


32 


34f 


18 


161 


m 


14 


2U 


16-i 


18 


25 


42 


36^ 


38g 


19ft 


181 


544 


14 


221 


16—1 


20 


274 


48 


411 


m 


214 


21i 


584 


If 


25 


20—1 


22 


294 


48 


42i 


m 


21s 


22 


61i 




27i 


20—1 


24 


3U 


52 


43i 


464 


241; 


22i 


641 


If 


29J 


20—1 


26 


m 


58 


50 


52 


26 


26 


724 


2 


31i 


24—1 


28 


36 


66 


56 


59g 


29S 


291 


m 


2 


334 


28—1 


30 


38 


72 


604 


634 


314 


32 


871 


2 


354 


28—14 




Double dash pot with screw lihin§ 
device 



s 


D 


A 


L 




H 


E 


Thick- 


DIam. 


Number 


















Diam. 


Heiglit 








Distance 


ness of 


of Bolt 


and Size 


Size 


of 

Flanges 


Face to 
Face 


Length 


WiJIh 


Height 


Centre to 
Inlet 


Flanges 


Circle 


of Bolts 


4 


9 


94 


144 


9 


144 


41 


1 


74 


4-1 


5 


10 


11 


14| 


lOi 


161 


54 


* 


84 


8-fe 


6 


11 


13 


165 


Hi 


19 


64 


s 


94 


8^ 


8 


134 


18 


21| 


16 


25 


9 




113 


8-g 


10 


16 


19 


24g 


18 


28t 


94 


14 


14i 


12-f 


12 


19 


20 


284 


20 


291 


10 


14 


17 


12-f 


14 


21 


23 


32| 


234 


34 


114 


u 


181 


12-S 


16 


234 


27 


36i 


274 


42 


134 


14 


m 


16-J 


18 


25 


30 


40J: 


31 


44g 


15 


14 


221 


16-1 


20 


274 


34 


444 


34| 


51 


17 


11 


25 


20-1 


22 


294 


36 


49i: 


36i 


56 


18 


1* 


27J 


20-1 


24 


314 


37 


49g 


38J 


58 


184 


n 


29i 


20-1 


26 


331 


42 


55 


42 


63 


21 


2 


3U 


24-1 


28 


36 


46 


59 


46 


67 


23 


2 


334 


28-1 


30 


38 


50 


63 


50 


72 


25 


2 


354 


28-14 



NOTES ON POWER PLANT DESIGN 69 



FLOW OF STEAM IN PIPES 

The area of a steam pipe, if the pipe is of short length, may be calculated by dividing the 
volume of steam to be delivered per minute by an assumed velocity of flow. For engines of the 
Corliss type taking steam in large quantities intermittently, a velocity not exceeding 6000 feet 
per minute may be used. A receiver having a volume equal to three times the capacity of the 
high pressure cylinder is sometimes placed close to the throttle valves of such engines. This re- 
ceiver furnishes a reservoir from which the engine draws steam; it enables a smaller steam pipe to 
be used and thereby -prevents the vibrations of the steam main which are so common in plants 
where slow speed engines are in use. For steam turbines or high speed engines which practically 
make a steady flow a velocity as high as 10,000 feet per minute may be used. The drop in pressure 
in a pipe of long length may be calculated by the formulae proposed by Mr. G. H. Babcock. These 
formulae are based on actual tests made on pipes up to 4" in diameter, and it is probable that the 
results will hold good for pipes of even larger size. Similar tests were conducted by R. C. Carpenter 
and a formula derived which is practically the same as that proposed by Babcock. In the formula : 

w = weight of steam in lbs. per minute. 

d = diameter of pipe in inches. 

L = length of pipe in feet. 

P = drop in pressure in lbs. per sq. inch. 

y = mean density in lbs. per cu. ft. 
V = velocity in feet per minute. 



V = 19,590 -^ 



Pd 



yL 1 + 



3.6) 
d 



W=87 



u-^ L ( 1 +• ■ 
P=. 0001321 \-}r 



VELOCITY OF EXHAUST STEAM 

The velocity of exhaust steam is taken from 6000 feet per minute for steam at 3 pounds back 
pressure to 40,000 feet per minute at a 29.5" vacuum. As the pressure gets lower the velocity 
increases, and some engineers use velocities which would increase from 20,000 feet per minute 
at a 26" vacuum to 35,000 feet per minute for a 29" vacuum. There has been in the past but 
little information as to the drop in pressure or the loss of vacuum due to these high velocities. 
Two series of experiments were carried on in the engineering laboratories at M.I.T. to determine 
the loss of pressure with such velocities. These experiments were with a pipe 6" in diameter. 

While the results apply specifically to a pipe of about this size it is probable that the equations 
may be used for pipes of larger sizes. No doubt the drop in pressure in the larger size pipe will 
be less than given by the equation. These experiments cover a range from a 25" vacuum through 



70 NOTES ON POWER PLANT DESIGN 

29H"- The formulae proposed are modifications of the Babcock formula and the letters used have 
the same tneaning, i. e.: 

L = the length of pipe in feet. 

y = the mean density of the steam in lbs. per cu. ft. 

V = mean velocity of the steam in ft. per min. 

P = difference in pressure in lbs. per sq. inch. 

d = diameter of the pipe in inches. 



Pd 
V = 13,700 xl o~ft"\ for straight pipe. 



„.L(l+ljl) 



P = .0001791 Tr ^ for straight pipe. 

y d^ 



Pd 
V = 9600 \ o-g \ for a 90° elbow. 



Pd 

V = 7200 \ 3~6~\ ^^^ ^^^ ^^° elbows making a return bend. 

yLii+-j-) 

The accuracy of the work does not warrant calculation of results within velocities of 500 feet 
either side of the true velocity. 

Problem to Illustrate Application of Formula. Suppose that the exhaust pipe leading from 
a turbine to a condenser is 15' long, 20" diameter, with an elbow at each end. If it be assumed 
that the steam has a mean velocity of 30,000 feet per minute, what will be the drop in pressure 
between the turbine and the condenser? The vacuum midway between the turbine and the con- 
denser being 28^", barometer 29.95". 

The absolute pressure is .933 lbs. and the specific volume of steam at this pressure is 355 cu. ft. 



P X 20 
For the straight pipe 30,000 = 13,700\ -^ 

■ - ^5-5X1^(1 + 

P = .012 lbs. 



/ Px20 
For each elbow 30,000 = 9600 \-j — o 

X2(l+- 



3.6 \ 
20 / 



355 ' ' 20 

P = .003 

Note: — The length of the elbow is taken as 2 ft. along the center line. 
The total loss is .012 + .003 + .003 = .018 lbs. 

•018 n.// f 

= .04 of mercury pressure. 



.491 



The loss resulting from an elbow is equivalent to the loss in a piece of straight pipe having a length 
a little greater than twice the distance along the center line of the elbow. 



NOTES ON POWER PLANT DESIGN 71 

Example to Illustrate 

An engine is connected to a barometric tube condenser through 40 feet of vertical pipe, 10 
feet of horizontal pipe and three elbows; one elbow being located at the exhaust opening of the 
cylinder and the second and third elbows being on the vertical pipe leading to the condenser. 

The exhaust pipe is 12" diameter and the vacuum to be maintained is 26", with the bt rometer 
at 30.1". If the maximum difference in pressure between the condenser and the engine is to be 
not over .1" of Hg. how many pounds of steam per hour can be put through this 12" pipe? 

The length through the center of a 12" elbow is about 1 foot so that about 1x2x3=6 feet 
should be added to the length of the pipe making a total of 56 feet. 



.0491 X 12 
V = 13,700 \~i g-^rv r = 16,150 ft. per min. 

^^^^i+T2-; 



172 
16150 X .7854 x 60 



172 
Had .2" mercury been the greatest drop allowed 



= 7370 lbs. 



1.2 X .491 X 12 X 172 
V = 13,700 \ g-g^ V = 22,850 



56(1+ ^2 



and 10,400 lbs. could be taken care of through the 12" pipe. 



72 NOTES ON POWER PLANT DESIGN 



FEED WATER HEATERS 

Feed water heaters are of two classes, open heaters and closed heaters. 

In an open heater the water can not be heated above 212° while in a closed heater higher 
temperatures than 212° are possible. 

A primary heater is a heater placed on the exhaust pipe between the main engine or turbine 
and the condenser. 

A secondary heater which may be either an open or a closed heater utilizes the heat of the 
auxiliaries, exhausting at atmospheric pressure, in raising the temperature of the water leaving the 
primary heater to a temperature within 8 or 10 degrees of that of the exhaust steam. From the 
secondary heater the water passes through the economizer (if one is used) to the boiler. 

A feed water heater is very much like a surface condenser and consequently the same laws, 
regarding the interchange of heat per square foot of surface per degree difference of temperature, 
apply. 

The interchange of heat in condensers was found to be proportional to the square root of the 
velocity of the water through the tubes. Feed water heaters designed for torpedo boats, etc., 
where space is very limited have been made with the water flowing at high velocity in the annular 
space between two tubes placed one inside the other. The high velocity of water gives a large 
interchange of heat but requires 8 or 10 lbs. additional pressure on the pump forcing the water 
through the heater. 

The C. H. Wheeler Co. use the following formula in figuring the surface needed in a closed heater: 

S = sq. ft. surface 
W = lbs. of water per hour 
ts = temperature of steam °F. 
tc = temperature of cold water entering °F. 
th = temperature of hot water leaving °F. 
K = constant of transmission taken as 250 

>S ^ 2.3026 logio ^^ ~ ^" 



K ^^" ts-tk 

It is always safer to put in a larger heater than appears at first to be necessary. 
Tables of dimensions of both a Primary and a Secondary heater are given. These tables 
will give the general dimensions only. 

The feed piping at a heater should be arranged so that in case of any trouble with the heater, 
the water can be by-passed around the heater. This necessitates three valves. The piping must 
be of brass in order to resist the action of the hot water. 



NOTES ON POWER PLANT DESIGN 



73 




VIS 

1 

"-1 


SHELL. 






TUBES. 




N 


PIPING 


' 


Capacity in gallons 

at 

one filling. 


■5 

% 


2 i 
5 5 


J3 

2 


B 

s 


a 


J2 


2 .2 
"5 


. ,, Heating 
Surface in 
sq. ft. 


it 




■i 


30 


I_2 


20 


"K 


15 


21 


25 


II.6 




4 




6.0 


33 


40 


12 


24 


■M 


■5 


25 


31 


.14.3 




4 




9,8 


39 


50 


• 14 


28 


i>. 


17 


29 


41 


18.7 




5 




■63 


45 


6o 


14 


31 


I'A 


17 


32 


45 


20.7 




5 




18,0 


48 


75 


14 


38 


I'A 


17 


39 


55 


253 




5 




21.9 


55 


loo 


16 


40 


2 


i5 


41 


54 


329 


'K 


■6 




28.0 


58 


•50 


16 


S6 


2 


i5 


57 


76 


46.0 


IK 


6 




393 


74 


20O 


20 


44 


2 


28 


45 


105 


6J.4 




8 




45-6 


67 


250 


20 


54 


2 


28 


55 


126 


76.2 




8 




57 7 


77 


300 


25 


45 


2 


40 


46 


152 


92 


2'A 


10 


I, '2 


768 


72 


350 


25 


53 


2 


40 


54 


180 


1088 


2!^ 


10 ' 


iK 


895 


80 


400 


«o 


48 


2 


50 


49 


204 


1233 


2>i 


10 




121. 8 


78 


500 


30 


S8 


2 


50 


59 


24s 


147.0 




12 




147-8 


88 


600 


30 


61 


2 


55 


62 


282 


171. 7 




1 2 




151.8 


9' 


700 


34 


58 


2 


68 


59 


333 


201 5 




1 2 


2 'r, 


1868 


94 


800 


34 


68 


2 


68 


69 


391 


2364 




12 


^'A 


219,1 


104 


900 


34 


75 


2 


68 


76 


420 


254 




'5 


VA 


241.8 


HI 


1000 


34 


82 


2 


68 


83 


469 


282.9 




'5 


2'A 


264.2 


118 



s. ^ 



300 

435 
625 

700 
750 
87s 
idbo 
1300 
1650 
1650 
2450 
3470 
3800 
4000 
4:50 
50CO 
5JOO 
5700 



In computing the heating surface of the above table 15 per cent, is added for the corrugations. 



74 



NOTES ON POWER PLANT DESIGN 




Secondary Heater. 



o 
ID 

25 


f 1 


.0 £j 

i S 
z 


"0 ^ 


c 

5 « 

'5 •" 



Total Hcatiup 

Surface, 

Allowing 15 

per cent. Tor 

Corruantioii'i' 












SIZES 


IN INCHES. 










F. 


c. 


H. 


K. 


L. 


M. 


N. 





p. 


R. 


s. 


T. 


10 


9 


26 


■)< 


,8.89 


I 


5 


I 


■ 4?i 


49 


8 


.7?^ 


36 'i 


'i'4 


42!..; 


's'4 


10 


50 


12 


12 


37 


''A 


16.69 


I )-> 


6 


154 


16% 


63 


8 


'9'. 


48M 


14 


55 '4 


n'4 


II 


60 


12 


12 


45 


'/2 


20.30 


''A 


6 


>K 


16% 


71 


8 


'9 '-J 


Sf-'A 


14 


63>4 


■7'i 


"/ 


80 


12 


12 


60 


iH 


27.06 


'A 


6 


'.M 


16I4 


86 


8 


'9'.- 


T'i 


14 


78 '4 


■7 ''4 


■' 


100 


12 


12 


74 


iJi 


33.38 


''A 


6 


1^4 


16% 


100 


8 


'9'j 


85)4 


14 


92>:i 


'7 '4 


-' 


'50 


'5 


24 


60 


iK 


54.05 


2 


8 


IM 


20 


92 


9 


23?^ 


72H 


■7. 


82^4 


20 '-J 


>3 


200 


18 


36 


50 


I>s 


67.68 


2J^ 


10 


''4 


23!-i 


89 


12 


29'.. 


(>sX 


21' 


77 'i 


25 


>5 


250 


18 


36 


62 


■x 


83.91 


'2H 


10 


i.M 


23.'< 


101 


12 


29>;; 


nX 


21 


89<A 


25 


'5 


300 


18 


36 


74 


I>5 


100.17 


2y, 


10 


•J4 


23>< 


I '3 


12 


2g'A 


,»9X 


21 ■ 


101 '<: 


25 


'5 


350 


22 


54 


58 


I>« 


"7-77 


2K 


12 


i>^ 


27 


104 


14 


34 Ji 


77 


24J^ 


90 M 


29^ 


18 


400 


22 


54 


66 


Ij^ 


134.00 


3 


12 


i.'4 


27 


112 


14 


34 ?i 


85 


2AX 


98^ 


29 j<; 


18 


500 


24 


63 


72 


IK 


170.56 


3 


12 


iK 


30 


122 


16 


40 14 


92Ji 


i7</i 


107 


33 


18 


600 


27 


84 


64 


■H 


202.14 


3 


14 


3 


34 


121 


18 


43>i 


87 '4 


i\ 


104 


37 


21 


700 


27 


84 


74 


1>< 


233.74 


4 


14 


2 


34 


'31 


18 


4ih 


97 J4 


31 


114 


37 


21 


800 


30 


102 


70 


iK 


268.48 


4 


14 


2 


38 


'33 


20 


49 


95 


34 


114 


Ai'< 


21 


tyxi 


30 


102 


80 


i>i 


306.85 


4 


"4 


2 


38 


143 


20 


49 


'05 


.34 


124 


41 'i 


21 


1000 


32 


114 


78 


Ijo 


334.36 


4 


18 


2 


40 


■43 


20 


51 


103 


34 


124 


42)-. 


26 


i;oo 


i' 


114 


94 


'X. 


402.97 


5 


18 


2 


40 


■59 


20 


51 


119 


34 


140 


42'; 


26 


1500 


36 


144 


93 


'>2 


503.59 


5 


24 


3 


44 


162 


22 


57 


119 


39 


144 


44 


32 


2(KJC> 


36 


144 


124 


•IX 


671.80 


5 


24 


3 


44 


192 


22 


58 


.50 


J9 


■75 


44 


32 


300*1 


48 


258 


104 


'.'<; 


1008 96 


6 


30 


3 


56 


181 


24 


66 


130 


45 


160 


48 


38 


40(xj 


48 


258 


138 


1 <4 


1338.87 


6 


30 


3 


56 


211 


24 


66 


164 


43 


194 


48 


38 


5o<-io 


60 


402 


111 


''A 


1677.99 


8 


30 


3 


68 


202 


26 


72 


•43 


47 


«7S 


52 


38 


6000 


60 


402 


13s 


''A 


2038.51 


8 


30 


3 


68 


226 


26 


72 


167 


47 


199 


52 


38 



A type of feed water heater which has been recently developed by Shutte and Koerting Co. 
for use in battleships, torpedo boat destroyers and places where saving of space is an item, is shown 
by the sectional cut which follows. 

In this type of heater, the water to be heated is sent through a narrow space between sets 
of corrugated tubes. The lower tube in the cut referred to shows one set of tubes in section. The 
steam which heats the water is on the outside of the larger corrugated tube and on the inside of 
the inner corrugated tube. The feed water is sent through these tubes under high velocity and, 
due to the fact that the water is broken up into a thin film, it is possible to heat it to within a very 
few degrees of the temperature of the steam. The loss in head in passing the water through the 
heater may be as great as 12 pounds. Dimensions of the different sizes of the heater, together 
with the horsepower rating may be obtained from the diagram and table which accompanies the 
same. 



NOTES ON POWER PLANT DESIGN 



75 










DIMENSION 


TABLE 








(Boil 


sr Horse Power 








Feed Water 






Size 


at 3# back 








Connections 


Steam 


Drain 


No. 


Pressure 


A 


B 


E 


FWI FWO 


S 


D 


1 


80 


5'1" 


lOK" 


4' VA" 


1" 


2" 


1" 


2 


160 


5'1" 


14" 


4' VA" 


lA" 


3" 


1" 


3 


330 


5'1" 


17" 


4' VA" 


lA" 


3" 


IJi" 


4 


500 


5' 3" 


21" 


4' 2" 


2" 


4" 


lA" 


5 


650 


5' 3" 


22" 


4' 2" 


2" 


4" 


m" 


6 


830 


5' 3" 


24" 


4' 2" 


2" 


4" 


lA" 


7 


1000 


5' 5" 


24" 


4' 2K" 


3" 


5" 


2" 


8 


1150 


5' 5" 


27" 


4'2M" 


3" 


5" 


2" 


9 


1300 


5' 5" 


27" 


4' 2A" 


3" 


5" 


2" 


10 


1500 


5' 7" 


28" 


4' 3" 


3H" 


6" 


2A" 


11 


1660 


5' 7" 


28" 


4' 3" 


3^" 


6" 


2A" 


12 


2000 


5' 7" 


30" 


4' 3" 


3>^" 


6" 


2A" 


13 


2330 


5' 9" 


33" 


4' 4" 


4" 


7" 


3" 


14 


2700 


5' 9" 


33" 


4' 4" 


4" 


7" 


3" 


15 


3000 


5' 9" 


36" 


4' 4" 


4" 


7" 


3" 


16 


3300 


5' 11" 


40" 


4' 5" 


4>^" 


8" 


3H" 



76 NOTES ON POWER PLANT DESIGN 



COOLING TOWERS 

The amount of water surface in a cooling tower working with forced air circulation varies 
from 23 to 27 square feet per I. H. P. More surface is needed in a natural draft tower than in 
a fan tower, in general the surface being double that of a forced draft tower. The amount of air 
needed depends to a large extent upon the humidity of the air entering the tower. The air leav- 
ing the tower is either saturated or nearly so. 

It is not advisable to send an abnormal amount of air through a tower, as the cost of the in- 
creased poAver needed to run the fan and the greater shrinkage due to evaporation, amount to more 
than the gain made by the increased vacuum on the engine, resulting from the cooler circulating 
water, will offset. 

The materials used inside of a cooling tower to expose as large a surface of cooling water as 
possible to contact with the air without at the same time obstructing the free flow of air, are tiers 
of the tile pipes 6" diameter, 2 feet long, used by the Worthington Company, galvanized iron wire 
screens set nearly vertical, used by the Wheeler Company, galvanized iron troughs set horizontally 
and arranged so that the water flows from trough to trough as it descends (Jennison tower), boards, 
brush, or other material. 

The amount of air to be supplied to a tower and the shrinkage of water from evaporation 
may be calculated approximately from the following equations: 

Z = weight of cooling water entering condenser per lb. of steam. 

E = weight of water evaporated from tower per lb. of steam condensed. 

Yc = cu. ft. of cold air entering tower per lb. of steam condensed. 

This air may enter by natural draft, or as is most often the case it may be sent 
in by disc fans. 

Yh= cu. ft. of hot air leaving tower per lb. of steam condensed = 1, 

i- e 



Y = the wt. of air entering the tower may be figured thus: 

Vc ^ Vc 

29.92 X 12.39 Tc ^^, To 
.954 



491.5 Pc P, 



Tc = absolute temperature of air entering. 

Pc = absolute pressure of air entering tower in ins. of mercury. 

If the excess pressure of the air entering the tower is measured by the difference 

of water level in a U-tube, Pc = the sum of the barometer reading and — r^ times the 

difference of water level. This excess pressure can usually be neglected. 

Qh and Qc are the heats of the liquid corresponding to the temperatures of the hot and cold 
condensing water. 

Yh and Yc are the weights of water carried by a cu. ft. of saturated air at temperatures th and 
tc respectively. See curves 

Z X {Qh- Qc) = ^% X .24 (th -tc) +r (.90 xVhYh- relative humidity x Vc Yc) 

th and tc are temperatures of air at top of tower and at entrance to tower, r is the heat of 
evaporation corresponding to the temperature of the air at top of the tower. The temperature of 
the air at the top of the tower is from 10 to 25 degrees lower than the temperature of the hot con- 
densing water taken where it enters the tower. 



NOTES ON PO^VER PLANT DESIGN 77 

In making a calculation for a tower it is probably safe to assume a difference of 15 degrees. 
The air leaving the tower may be saturated or only partially saturated, the condition depending 
upon the amount of air sent in and the design of the tower. In general it is a good plan to assume 
that the air at the top of the tower is only 90% saturated and that the temperature of this air 
is 15 degrees lower than the temperature of the hot water entering the tower. These assumptions 
have been made in the calculations which follow. 

E = .90x Vk Yh - relative humidity x Vc Yc 

In the case of a jet condenser the steam condensed adds one pound to each Z pounds of cooling 
water entering the condenser. 

If E is greater than one pound then the excess must be supplied as make-up water. 
For a surface condenser E represents the make-up water. 

Problem. 

A cooling tower receives water from a surface condenser at 122° F., the water leaves the cooling 
tower at 90° F.; temperature of outside air 72°, relative humidity 80%. 

Temperature of condensed steam 95°, vacuum in condenser 25", barometer 29.7". 

Engine of 500 H. P. and consumes 20 pounds of steam per H. P. 

What is the amount of air needed per pound of steam condensed and what is the per cent 
loss of cooling water due to evaporation? 



1053.2 - 63.1 990.1 



31.8 = Z 

Vc X 566.5 X .00347 



90.0 - 58.1 31.9 



^^^•l = .754 x'531.5 X -24 I (122 - 15) - 72 I + 1031.8 j .9 ^3^^ 

- .SVcX .00124 



29.7 



The figures .00347 and .00124 are the lbs. of water required to saturate a cu. ft. of dry air at 
107 and at 72 deg. respectively. The figure 1031.8 is the value of the heat of vaporization at 
107°. 

990.1 = 3.036 Vc Vc = 326 cu. ft. 

E = (.00333 - .00099) Vc = .763 lbs. evaporation per lb. of steam condensed or per 31.8 lbs. of 
circulating water. 

This is „ p = .0240 or 2.40% shrinkage. As the first term of the right hand side of this equation 

ol . o 

evaluates .623 Fc it is evident that the heat carried off by the air is 5^1-5^ percentage of the total 

amount abstracted. This figiires as 20.5%; the heat taken out by evaporation being 79.5%. 

To illustrate more fully the use of the equation and to illustrate also the extra cost (at the cooling 
tower) of a high vacuum over a moderate vacuum, two cases will be taken up : First a condensing 
and cooling outfit maintaining a 28" vacuum and, second, a similar outfit maintaining a 26" vacuum. 

The illustration will be worked through for each case with relative humidities of the enter- 
ing air as 90, as 70, and as 50% 

First case — A condenser maintaining a 28" vacuum with hot condensing water at 95^ or 
7 degrees below the temperature corresponding to the vacuum. The exhaust steam is assumed 
to contain 4% of moisture. The temperatin-e of the air may be taken as 72° and it will be assimaed 
that the tower is to cool the water to this temperature. 

For air 90% saturated at 72° the volume required per pound of steam = Vc may be cal- 
culated thus: To abstract the heat from a pound of exhaust steam 43.5 lbs. of cooling water would 



.78 NOTES ON POWER PLANT DESIGN 

be the minimum weight required, since 1000 heat units are to be abstracted from each pound of 
steam with an increase in temperature in the circulating water of 23°. 

) ' 29.92 ] 

' - .9 Fc X 0.0124 

1000 = .143 Vc + 1046.6 (.00144 - .00112) Vc J 

1000 = .143 Vc + .335 Vc Vc = 2100 cu. ft. 

The evaporation = .00032 x 2100 = .672 lbs. 

Of this total heat abstracted the heating of the air accounts for 30 per cent and the evaporation 
70 per cent. 

Similar calculations for 70 per cent and for 50 per cent humidities give 



Per cent 


Cu. ft. air 


Evap. per lb. 


Per cent heat 


Per cent heat 


humidity- 


per lb. of 


of exhaust 


abstracted by 


abstracted by 


entering air 


exhaust 


condensed 


the air 


vaporization 


90 


2090 


.672 


30 


70.0 


70 


1350 


.770 


19.4 


80.6 


50 


990 


.812 


14.1 


85.9 



Second: Suppose that the vacuum to be carried is 26" with air at 72° and hot condensing 
water at 119° or 7 degrees below the temperature corresponding to the vacuum. Cold water at 
72°; and 4 per cent moisture in the exhaust steam. 

The heat to be abstracted per pound of exhaust is 983 B. T. U. and 20.9 lbs. of cooling water 
is the minimum required per pound of exhaust. From calculations similar to the preceding it 
appears that the amounts of air needed and the evaporations are: 



lative 


Cu. ft. 


Evaporation 


Per cent heat 


Per cent heat 


nidity 


air 


in pounds 


abstracted by 
the air 


abstracted by 
vaporization 


90 


386 


.737 


22.5 


• 77.5 


70 


350 


.756 


20.8 


79.2 


50 


321 


.773 ~ 


18.7 


81.2 



The amount of water evaporated per pound of steam condensed is about the same in each case. 

In the first case with 70 per cent humidity the evaporation was .770 in 43.5 lbs. of water sent 
into the tower, or 1.8%. 

In the second case with 70 per cent humidity about 3.6%. 

The curve showing the pounds of water needed to saturate one pound of air at any tempera- 
ture may be constructed very quickly from values taken from any steam tables. 

Example. — The amount of water required to saturate one cubic foot of air at 88° F. is .002 
lb. If the air was of a relative humidity of 60 to start with, then 40 x .002 would be the amount 
the air would take up in becoming saturated and the B. T. U. abstracted would be 

1042.2 X .40 X .002 = .834 per cu. ft. of air. 



PER CENT OF ENGINE POWER REQUIRED BY COOLING TOWER FAN AND BY 
THE EXTRA DISCHARGE HEAD ON THE CIRCULATING WATER 

Referring to the first case already cited, with relative humidity of 70, 1350 cu. ft. of air were 
needed. Suppose a disc fan is to be used and a dynamic head of .3" of water maintained at the 
fan. As the static head is zero the velocity head will be .3". 

This velocity pressure corresponds at 70° to a velocity of 2200 ft. per minute. Suppose the 



NOTES ON POWER PLANT DESIGN 79 

engine uses 14 pounds of steam per H. P. per hour, then the steam per minute is 14/60 lbs. and 
the cu. ft. of air sent through the tower is 14/60 x 1350. 

The H. P. input to the fan is, for this case, if 30 per cent is assumed as fan efficiency: 

of engine power. 

To this should be added the power due to pumping 14/60 x 43.5 pounds of cooling water 
per minute through an additional head of about 30 feet. This amounts to .00889 H. P. 

If the fan were driven by a small engine using 35 pounds of steam per H. P. hour and the 
circulating apparatus were also steam driven using 40 lbs. per H. P. hour, then the extra steam 
required by the cooling tower outfit would be 

2 10 
.050 X 35 + .0089 x 40 = 2.10 and -jj- = .15 or 15.0 per cent additional. 

A similar calculation for the second case with 26°" vacuum, 70% humidity with engine using 
15 pounds of steam per H. P. hour gives: 

15 
Air per minute = ttkX 350 
60 

.3 X 5.2 X ^ X 350 
H- ^- *^ ^^^ = 33000 X .30 = -^^^^ 

20.9 x^ X 30 
Extra H. P. on circulating pump = oonnn ^ .00472 

If fan engine and circulating apparatus were steam driven then using same rate as before 

.0137 X 35 + .00472 x 40 = .668 
.668 



15 



= .0445 or about 4.45% additional. 



If the cooling surface used in the tower offers much resistance to the free discharge of air from 
the fan through the tower, it may be necessary to run the fan at higher velocity which increases 
the work of driving. 

In the Wheeler Barnard cooling tower the cooling surface consists of galvanized wire screens 
placed in parallel vertical rows about 3" apart. Water is distributed to the tops of these screens 
bj^ U-shaped troughs each trough supplying two screens. In this way as each side of a screen is 
figured as coofing surface, 8 sq. ft. of surface is obtained per cubic foot of volume in the screen 
section of the tower. But little resistance is offered to the passage of air between the screens. 

From experiments made by the company it is found that ordinarily eleven feet of vertical length 
of screen offers sufficient evaporating surface to saturate the air. The tower is square or rectangular 
in section and the number of fans needed depends upon the size of the tower. 

The B. T. U. per hour per square foot of surface in a cooling tower apparently varies from 200 
to 900. 

It is not possible to get figures for a square foot of surface which will apply to every type of 
tower since with different kinds of surface there is a variable amount of spraying; even with the 
same surface this spraying varies with the quantity of water flowing; and consequently there is 
available an unknown amount of surface besides that provided in the tower. 

A drop of water .178" in diameter weighs .75 grains and the surface of a number of drops suffi- 
cient to make a gallon would be about 54 square feet. 

Cooling towers are occasionally placed on the roof of buildings. By using a surface condenser 



80 NOTES ON POWER PLANT DESIGN 

the extra work on the up leg of the circulating water is practically offset by the gain from the down 
leg and there is simply the friction hi the extra lengths of pipuig to make additional work for 
the circulating pump. 

Where one tower is used for a number of condensers having centrifugal circulating pumps it 
is advisable to have a separate discharge pipe from each centrifugal to the tower. 

Towers cost above the foundation from $2.60 to $4.00 per K. W. capacity. 

SPRAY NOZZLES 

By spraying water into the air a cooling may be effected through the evaporation of a part 
of the water just as was the case in the cooling tower. 

The total exposed surface of the sprayed jet meets less air per pound than in the cooling tower, 
and on this account it is often advisable to spray 30 to 50 per cent of the water a second time before 
sending it through the condenser. 

Generally spray nozzles of the size known as 2" are the most economical. The 2" size screws 
on to a 2" outlet; the opening in the nozzle tip being about .8". As many nozzles should be pro- 
vided as are needed to discharge the entire weight of condensing water under a pressure of not 
over 15 lbs. gage at the nozzle. 

The nozzles should be set from 8 to 10 feet apart if 2"; a greater distance if over 2". Where 
a considerable number of nozzles are used it is customary to have the water which is sprayed into 
the air fall back into an artificial pond one or two feet deep. When a number of nozzles are in use 
the aspirator action exerted by the jets causes a current of air to flow along the surface of the pond 
from the edge towards the centre. This current of air assists to some extent in the cooling. 

In some few instances spray nozzles have been put along the edges of a narrow brook and the 
falling spray caught on board fences inclined 30° with the ground and draining into the brook. 

There are one or two small plants where the cooling nozzles discharge on to the roof of the 
building. From tests made in the Engineering Laboratories of the Massachusetts Institute of 
Technology on the Schutte Koerting nozzles it seems that 

1° The temperature of the water after spraying is more dependent upon the temperature 
and humidity of the atmosphere and upon the fineness of the spray than upon the initial tem- 
perature of the water. Therefore it is advisable to spray -the water as hot as may be without 
excessive steaming. 

2° At high humidity, 80% or 90%, the temperature of the water, may be lowered to within 
12° F. or 13° F. of the temperature of the air, with a total drop in temperature of 35° F.. to 40° F. 

3° At low humidity 20% to 30%, the temperature of the water after spraying may be as much 
as 8° F. below the temperature of the air and the total drop in temperature 40° F. to 45° F. 

4° The loss of water by evaporation is approximately .15 pounds per degree lowering of 
temperature per 100 pounds of water discharged, or a gross loss of about 6% for 40° F. lowering 
of temperature. In no case was the loss found to exceed 7%. 

The discharge of these nozzles was found to be as follows: 



Head in ft. 


Cu. 


ft. per 


Cu. 


ft. per min. 


Cu. ft. per mm. 


at base of 


min 


.. for 1" 


for 2" pipe 


for 3" pipe 


nozzle. 


pipe. 


Diam. 


Tip = 


= .800" diam. 


Tip = 1.181" diam, 




nozzle at 










tip 


.406" 








25 




1.782 




6.736 


14.83 


30 




1.952 




7.379 


16.24 


35 




2.109 




7.971 


17.54 


40 




2.254 




8.521 


18.75 


45 




2.391 




9.036 


19.89 


50 




2.520 




9.526 


20.97 


55 




2.643 




9.991 


21.99 


60 




2.761 




10.44 


22.97 


65 




2.873 




10.86 


- 23.91 



NOTES ON POWER PLANT DESIGN 



81 




Tempera/'ure of /J//-. 




82 NOTES ON POWER PLANT DESIGN 



CENTRIFUGAL PUMPS 

Centrifugal pumps either single or multistage are replacing the reciprocating piston pump 
for pumping condensate, circulating water and feed water. 

Centrifugal pumps should have the impeller designed for the conditions of suction head, de- 
livery head, speed and capacity the pump is to work under. Well designed pumps give efficiencies 
of from 75 to 80 per cent. 

The centrifugal pumps of five stages used in the high pressure fire service in the City of New 
York showed under test efficiencies of 75 and 77 per cent when working with delivery pressures 
of 300 lbs. 

Centrifugals are sometimes arranged so that two pumps driven by the same shaft may deliver 
into a common discharge, thus giving a large quantity at a moderate pressure; or the discharge 
of one may be sent into the suction of the other and the delivery pressure increased ; the quantity 
of water being, of course, decreased. 

If the efficiency of each pump is 71 per cent the efficiency of the outfit used either way will 
remain practically the same. 

In pumping circulating water from a jet condenser to a cooling tower, as there is less than 
atmospheric pressure on the suction side of the pump, the total static head should be calculated 
from the difference of the absolute pressures at entrance to and exit from the pump. To this head 
expressed in feet should be added an amount sufficient to allow for the friction and other losses. 

The efficiency of the smaller pumps is probably not over 60 per cent. 

The velocity of water in the discharge pipe should not exceed 400 feet per minute; 6 feet a 
second is a velocity quite commonly allowed. 

Although a number of centrifugal pumps connected to jet condensers may work successfully 
when piped to a common discharge leading to a cooling tower, it is always safer to connect each 
centrifugal with the tower through a separate pipe. 

Turbine driven stage centrifugals are quite generally used now in the large boiler plants in 
place of the steam or power driven reciprocating feed pump. The hot feed water must conie to 
the pump under a head. The efficiency of centrifugals used as feed pumps may be assumed to be 
between 40 and 55 per cent; 45 per cent has been used as the efficiency in the calculation for horse 
power input given below. 

The maximum horse power input required by a centrifugal boiler feed pump is 

r^ X T , T- J T^ TT Ti • X 2.32 X Gage Pressure x 30 x Max. Boiler H. P. 
Centrifugal Feed Pump H. P. mput = 33 000 x 60 x 45 

7.8 X Gage Pressure x Max. Boiler H. P. 

lopoo ^ "PP^^^- 

Centrifugal pumps have to be primed (filled with water) before starting. This may be done by 
putting a foot valve on the end of the suction pipe and then filling with water under pressure, the 
air at the top of the casing being vented, or the pump may be primed by closing a valve in the 
delivery pipe and then exhausting air from the top of the pump casing by a steam ejector, a water 
ejector or by means of a connection to a dry vacuum pump. 

As a foot valve offers considerable resistance to the flow of water it is to be avoided whenever 
possible; should it be necessary to use a foot valve one at least two sizes larger than the suction 
pipe is to be recommended. 

Centrifugal pumps of large capacity either turbine driven or motor driven have been used as 
pumping units in municipal pumping stations. While it is not possible to get as high a duty as 
may be obtained with a reciprocating pump the first cost is only about one third that of the recip- 
rocating and the number of operatives required to run the centrifugal outfit is less. 

These pumps should have both a check valve and a hydraulically operated discharge valve 
in the discharge pipe. In shutting the pump down the discharge valve is closed before the power 



NOTES ON POWER PLANT DESIGN 83 

is shut off. While the pump might be stopped without closing this valve and the check valve de- 
pended upon to prevent a flow-back from the reservoir or standpipe, should this valve stick open 
and close suddenly the water hammer blow resulting could not be withstood by the pump or the 
piping. 

Pumps used for this service should have suitable characteristics. The pressure should not 
build up over 15 per cent when the discharge valve is closed with the pump running. 

Following are some characteristic curves obtained from test data on different types of pumps. 
All of these curves were plotted for a constant speed. The pumps would have different characteristic 
curves at every speed. These curves were plotted at the most economical speed of the unit. 

Fig. 1 shows the curves taken from a Worthington Tri-rotor pump. This pump was con- 
nected to an 800 H. P. Curtis Turbine and installed for the Carnegie Steel Company for pump- 
ing dirty water. This pump has no discharge valves and gives an efficiency of 74% which is high 
for a volute pump. 

Fig. 2 gives the curves of a DeLaval pump which are notable in that the power taken by the 
pump decreases rapidly after the point of maximum efficiency is reached. This allows of the 
installation of a motor which is just capable of handling the full load of the pump. 

Fig. 3 shows the characteristic curves for a Worthington Boiler Feed Pump installed at the 
Commonwealth Edison Company. The pump is of the double suction type in which water it 
admitted to both sides of the impeller. This pump has three stages and is connected to a 150 
H. P. Curtis Turbine running at 2350 R. P. M. The feature of the characteristics is the wide 
range of discharge over which the efficiency is high. 

Fig. 4. The set of curves was taken from a double stage Alberger Fire Pump which runs 
at a speed of 1400 R. P. M. and requires a 90 H. P. motor. The high efficiency of this pump is 
notable for a double stage pump. These curves also show what would take place if the discharge 
piping should fail while the pump was in operation. The head would, of course, fall nearly to zero 
and the discharge would go up rapidly. The horse power taken from the motor under these con- 
ditions would increase rapidly due to the marked decrease in efficiency. In this set of curves the 
power supplied would be 107 at zero head and hence the 90 H.P. motor must be capable of sub- 
taining this overload of 17 H. P. for a short time. 

All centrifugal pumps operating under suction head must be primed before they can be started. 
All the passages of the pump must be completely filled with water before the pump will "pick 
up." It is dangerous in many cases to allow a pump to be started without priming, since many 
pumps are so constructed that they depend on the presence of water for running balance and inter- 
ference at the clearance spaces may destroy the pump if water is not present. 

The theory of centrifugal pumps with reference to the blade angles, calculation of pressures 
in the casing, and other points of design, is extremely complicated and based entirely on assump- 
tions as to existing conditions in the pump. 

The entrance angle of the impeller depends upon what assumptions are made in regard to the 
direction of absolute velocity at entrance. This velocity is usually assumed to be radial, and is 
taken as 15 feet per second for pumps without lift and 10 feet per second for pumps with lift. 

The construction of the blade is arbitrary to some extent. Some manufacturers use the arc 
of a circle, others an involute, and still others a logarithmic spiral. 

In the accompanying pruit oc represents the angle of entrance of the impeller and U the angle 
of entrance to the guide vanes. The effect of the shape of the blades on the exit and entrance velo- 
city diagrams is also shown in the print. 

The De Laval centrifugal is made with the angle at exit 20° with the tangent. 



84 NOTES ON POWER PLANT DESIGN 

In order to estimate the loss of head through friction in piping the accompanying chart taken 
from the catalogue of the De Laval Co. is quite convenient to use. 

If the quantity of water passing through the pipe and the size of the pipe are known, the fric- 
tion head in 1000 feet length of pipe is found by laying a straight edge through the known points 
of the scales representing capacity and size of pipe. The friction head is then read off on the third 
scale at the point of intersection between the straight edge and this scale. 

The values obtained from this chart are based upon the Hazen-Williams formula: 

0.63 /;jX 0.5* 0.12 

V = cr ( -y- 1 X 10 

where v is the velocity in feet per second, r is the hydraulic radius = t in feet, h the fric- 
tion head and / the length of piping, c is a constant depending upon the roughness of the pipe 
and upon the hydraulic radius. 

The formula can also be written 

147.85 _Q_y-852 

where h is, as before, the friction head in feet for / = 1000 ft., Q is the water quantity in gallons per 
minute and d is the diameter of pipe in inches. 

The chart is based upon a value of c = 100, which is mostly used and considered safe for ordin- 
ary conditions. 

1.852 

For other value of c the figure obtained from the chart should be multiplied by i^ = ( 

For information regarding coefficient c for different kinds and size of pipes, and also value of 
K for different values of c, see table below. 



Size of 
Pipe, inches 


2 to 3 


4 


5 


6 


8 


10 


12 


16 


20 


24 


30 


36 


42 


48 


54 


60 


c 


K Condition of pipe 






Year of Service for Cast Iron Pipe 
















140 


.54 Very smooth and straight 
and Brass, Tin, etc. 




00 


00 


00 


00 


00 


00 ■ 


00 


00 


00 


00 


00 


00 


00 


00 


00 


130 


.61.5 Ordinary straight Brass or 


Tin 















































120 


.715 Smooth new Iron 




4 


4 


4 


5 


5 


c 


5 


5 


5 


6 


6 


6 


6 


6 


6 


110 


.84 










10 


10 


10 


11 


11 


11 


12 


12 


12 


12 


12 


12 


100 


1.0 Ordinary Iron* 




13 


14 


15 


16 


17 


17 


18 


19 


19 


19 


20 


20 


20 


20 


20 


90 


1.21 














26 


27 


28 


29 


30 


30 


30 


30 


31 


31 


80 


1.51 Old Iron 




26 


28 


30 


33 


35 


37 


39 


41 


42 


43 


44 


45 


45 


46 


47 


60 


2.58 Very rough 




45 


50 


55 


62 


68 






















40 


5.45 Badly tuberculated 




75 


87 


95 



























00 indicates the very best cast iron pipe laid perfectly straight, and when new. 
indicates good new cast iron pipe. 



NOTES ON POWER PLANT DESIGN 



85 



/Sooots 



O.I 



- /ooooo 
Soooo 
Qooeo 
70000 
60000 

-Soooo 

-4.0000 

- 30000 



-,^0000 
/Sooo 



—/oooo 
Sooo 
sooo 

'7000 
6000 

—Sooo 



-4ooo 
-3ooo 

-Zooo 
/Soo 



-/ooo 
900 
Soo 
Too 
600 

— Soo 

4So 

—400 

3SO 

—3 00 



.:?oo 
/SO 



-100 

9o 

So 

7o 

60 
^So 









■ S6 

■9o 

■S4 

•73 

-7Z 

-66 

.60 

.£4 
-4-3 

-36 
-Jo 

-^o 

-/3 
■/£ 
■/4 



1? 



■/Z 



■/o 



■ 6 
-S 



-3 



\ 

\ 
\ 



oJS 

0.3 

OA 
oS 



\ 

\ 







0.6 — 



£7.7 
0.8 
0.9 

/.O — 



/.£ 



- s 



3.5- 

4- 

4-5- 



10 ■ 



Zo 



30 



40 






r ^ 



Chart for determining resistance of pipes to How of water, 



86 



NOTES ON POWER PLANT DESIGN 



/60 




aoo 



Q A*>e> gooo 3000 400a S009 6OO0 fooo 8000 Sooo /ooco /^eea /iooo /3000 /fooo /javo /sooo //oati 



NOTES ON POWER PLANT DESIGN 



87 



/80 



/GO 




8000 



aioo 



geoo 



eaoo 



s&oo 



3^00 



3400 



^600 



NOTES ON POWER PLANT DESIGN 



no 




/ao 



zoo 



300 



400 



JOO 



600 



SCO 



NOTES ON POWER PLANT DESIGN 



89 




90 



NOTES ON POWER PLANT DESIGN 



i/i = Linear i^e/oc/ty of irnpe/Ier at outer edge. 
Ttl = " " " " " inner " . 

Vea = Abso/ute ye/ocity at entrance (TaJcen rac//a/). 
Vrw== Veioc/ty of y/ater reiative to wbeei. 
Vab = Absoiute exit veiocity from impeiier. 

I^adiai y^eiociiy at entrance is usuaily fal<en 
at iS f.p.s. if ft? ere is no iift and iO f.p,s, if 
there is a iift. 




NOTES ON POWER PLANT DESIGN 



91 



COAL HANDLING, COAL BUNKERS 

FLIGHT CONVEYORS 

One of the oldest forms which, from its simplicity and comparatively low first cost, is still 
one of the most extensively used, consists merely of an endless chain to which are attached, at in- 
tervals, scrapers or flights. The improved forms of this conveyor, now most generally used, have 
sliding shoes or rollers attached to the flights or the chains, supported on runways. The flights are 
allowed to come very close to the trough bottom, but not actually in contact with it, thus reduc- 
ing the friction upon the trough to the minimum amount. 

The accompanying figure illustrates a single-strand flight conveyor. 



CONVEYING CAPACITIES ON FLIGHT CONVEYORS 
• S. R. Peck, A. S. M. E., 1910 

In tons (2000 pounds) of coal per hour at 100 feet per minute. 



Size 




Horizontal 






In 


clined 




of 




Spaced 




Lbs. per 


10° 


20° 


30° 


Flight 


18 Inches 


18 Inches 


24 Inches 


Flight 


24 Inches 


24 Inches 


24 Inches 


4x10 


33M 


30 


22M 


15 


18 


UH 


10^ 


4x12 


42^ 


38 


28H 


19 


24 


18 


1314 


5x12 


51M 


46 


34>^ 


23 


28H 


22K 


mvz 


5x15 


mu 


62 


46K 


31 


40>^ 


^m 


22^ 


6x18 




80 


60 


40 


49>i 


40H 


31J^ 


8x18 




120 


90 


60 


72 


57 


48 


8x20 






105 


70 


84 


66H 


56 


8x24 






135 


90 


120 


96 


72 


10x24 






172H 


115 


150 


120 


90 




, The horse-power required for handling anthracite coal may be determined from the follow- 
ing formula, this taking no account of gearing or other driving connections. 



H.P. = 



ATL + BWS 
1000 



T = net tons per hour. 
L = length, centre to centre, in feet. 
W = weight of chain and flights (both runs) in pounds. 
S = speed per minute in feet. 



92 NOTES ON POWER PLANT DESIGN 

A and B are constants depending on the inclination from the horizontal. (See value below.) 

Hor. 5° 10° 15° 20° 25° 30° 35° 40° 45° 

A 0.343 0.42 0.50 0.585 0.66 0.73 0.79 0.85 0.90 0.945 
B 0.01 0.01 0.01 0.01 0.009 0.009 0.009 0.008 0.008 0.007 

The common working speeds are from 100 to 200 feet per minute, and the capacities are as 
shown by the table, these conveyors in some cases handling upwards of 500 tons per hour. 

As an illustration, suppose it is desired to elevate hard coal 50 feet by a flight conveyor inclined 
30 degrees, the capacity of the conveyor being 30 tons per hour at 100 feet speed per minute. From 
the table it is evident that at a speed of 100 feet per minute the flight should be 6 inches by 18 inches 
and spaced 24 inches apart. 

The length of the conveyor, centre to centre, would be at least 100 feet. 

Calling the weight of the chain 20 pounds per foot, and the weight of the flights spaced every 
2 feet, 40 pounds, as given, the total weight per foot figures as 40 pounds. 

Substituting, in the formula given, the 

„ p _ 0.79 X 30 X 100) + (0.009 x 200 x 40 x 100) 
" 1000 

= 7.77 >. 



PIVOTED BUCKET CARRIERS 

Where the design of the plant requires conveying machinery adapted to the combined service 
of handling coal and ashes, the pivot-bucket carrier is hard to excel. The handling of ashes is very 
hard on conveying machinery, and the construction of the carrier permits replacement of the several 
parts as corrosion or wear proceeds. 

Pivoted-bucket carriers for elevating coal in power-plant service have become quite popular. 
Their advantages are slow speed, silent operation, adaptability to change of direction without 
transfer, high efficiency, and easy renewal of worn parts. Their disadvantages are danger of buckets 
sticking or upsetting and jamming in the supports, and the difficulty of preventing spill at the 
loading and turning points. Protection against jamming may be had by connecting with the 
driving machinery through a safety pin whose margin of strength beyond the power requirements 
is very slight; or better, by designing the supports so that the buckets will clear in whatever posi- 
tion they may come around. _ _ 

Uncleanly loading is guarded against in various ways in the several latest designs of carriers, 
of which the following may be noted. 

In the Hunt carrier, the buckets are spaced an inch or so apart and are loaded by a special 
device consisting of a series of connected funnels at the loading chute, in synchronism with, and 
dipping into, the carrier buckets, vso that each bucket receives its proper charge only. 

The Webster carrier has buckets with carefully planed lips, the pitch of the buckets being very 
slightly less than the pitch of the carrier chain links, thus depending on close contact to eliminate 
the leakage. 

The McCaslin carrier uses overlapping buckets. These lap the wrong way after tripping for 
discharge, and are reversed by a "righting mechanism" before again passing the loading point. 

The Peck carrier uses overlapping buckets similar to the McCaslin, but they are attached 
to the links extended beyond the points of articulation. This arrangement unlatches the buckets 
at the turns by giving them a path of greater radius than the chain joints, thereby doing away with 
a righting device otherwise necessary with the overlapping bucket. 

None of these devices for preventing spill at the loading and turning points are particularly 
effective. The difficulty is inherent in this type of conveyor whose many advantages, however, 
far outweigh their defects. 

The alternative of the pivoted-bucket carrier for handling coal is the standard arrangement 
of an elevator with rigid steel buckets discharging into a flight conveyor which crosses above the 



NOTES ON POWER PLANT DESIGN 



93 



bunkers, and is provided with discharge gates at convenient intervals ; or instead of a flight con- 
veyor, a belt with movable tripper. This is a well tried-out system, thoroughly reliable, and 
by many preferred to the run-around carrier, on the ground of lower first cost and simpler con- 
struction. The elevator conveyor system is not adapted to handling ashes, which, however, should 
be tr.ken care of by separate machinery whenever possible to do so. 




Diagram Showing Operation of the Peck Carrier, 

The general arrangement of a "rectangular" pivoted bucket conveyor is shown by the accom- 
panying cut. 

Coal discharged from a car or from a cart falls into a crusher where the large lumps are broken 
up. From the crusher the coal is taken directly into the conveyor or into the feeding mechanism 
which fills the conveyor. 

Somewhere in the system there must be a tightener, which in this cut is shown as located at 
the lower right-hand corner. 

The reciprocating feeder consists simply of a movable plate, at the bottom of the hopper, 
which is pushed forward and back through the action of an eccentric. On the forward stroke 
coal is fed into the crusher. The length of the plate is such that coal in the hopper will not flow 
over the left-hand edge when the feeding plate is still. 

When coal is discharged directly through the track hopper, feeder and crusher into the con- 
veyor buckets as shown in the cut, the track must be from 10 to 12 feet above the bottom run 
of the conveyor. 

Where there is not sufficient depth for this arrangement an apron feeder (see illustration) 
would be used to elevate the coal to the crusher. 

The speed of the apron must be regulated to suit the capacity of the carrier or a reciprocat- 
ing feeder may be inserted between the hopper and the apron. 



94 



NOTES ON POWER PLANT DESIGN 



STANDARD SIZES AND CAPACITIES OF PECK CARRIERS 



For a speed of from 40 to 50 feet per minute with pitch of chain 24 inches the capacity is 
with buckets 24" x 18" 40 to 50 tons coal per hour 

with buckets 24" x 24" 55 to 70 tons coal per hour 

with buckets 24" x 30" 75 to 100 tons coal per hour 

with buckets 24" x 36" 90 to 120 tons coal per hour 



XrHIMUM T CLEARANCE 



General Dimensions, 24-inch Pitch Carriers 




NOTES ON POWER PLANT DESIGN 



95 



The general dimensions of a Peck carrier 24" pitch may be obtained from the cuts shown on 
the preceeding page. 

The power required for driving a rectangular conveyor similar to those referred to may be 
obtained from the following formula which is based on tests made on a number of such conveyors. 
H. P. = .000085 X tons per hour x speed in feet per minute x elevation in feet. The power run- 
ning empty is approximately one-half of the power for loaded condition. The power required 
for an apron feeder may be calculated from the same formula. A reciprocating feeder requires 
about 5 H. P. 




A coal crusher of 30 tons capacity per hour requires a floor space of 7' x 4'-6" and height of 
3 feet overall when set on a cast iron base and 2 feet when set as shown in the cut illustrating the 
apron feeder. It requires 5 H. P. to drive it. 

A 50 ton crusher 10 H. P. with floor space 9' x 5' and heights of 3' 6" and 2' 6" according to 
setting. 




A 70 ton crusher 15 H. P. space 9' x 6' and heights of 4' 6" and 3' 6". 
The accompanying cut shows, a crusher with hopper and casing removed. 
A V bucket elevator conveyor is shown by the sketch on the page following, 
diagrams A-F indicate some of the possible arrangements. 



The small 



96 



NOTES ON POWER PLANT DESIGN 




'I -,^-^-cNj==^^-j:^iAsr; 



-i^^^-^i^jg^ 



f5=** 



W 



**=^ 




f?^ 



^ 



fP^TT? 



^^ 




Coal is fed to the lower run. by a plain chute, is then pushed along the run till the vertical is 
reached, where the coal is carried inside the buckets; on the upper run the coal is pushed along 
until it reaches an opening through which it is discharged. 

A 40 ton V bucket elevator installed at the Bergner and Engel Brewing Co.'s plant and a 
40 ton coal elevator and flight conveyor at the U. S. Arsenal at Frankford are shown by the cuts 
which follow. 




U. S. Arsenal. Frankford,. Phila. 



NOTES ON POWER PLANT DESIGN 



97 



A locomotive crane operating a grab bucket is frequently used to move coal from a storage 
pile onto a belt or bucket conveyor, for unloading barges, etc. 




-►--»— »-->•-»->— 



'>^- 



•<~« 



CONCRETE ■¥ STCEL COAL BUNKEII 
CAPACIir lOOOTONS 




WW 




\oo& 



Bergner and Engel Brewing Co., -Phtladelpiita, Pa. 
40 ton per hour v-bucket elevator. Conveyor for coal; push car and electric skip for ashes. 




Such cranes are either mounted on a car like a platform car or elevated as shown by the accom- 
panying figure. 

For unloading barges and hoisting coal to an elevator a tower known as the Boston tower 
is quite generally used. This handling device consists of a grab bucket operated from the tower, 
which has projecting out a distance of 20 or 30 feet, a horizontal arm on which travels a movable 
carriage through which run the hoisting ropes operating the grab bucket. This carriage may 
be moved out or in while the grab is being raised or lowered. 



98 NOTES ON POWER PLANT DESIGN 

BELT CONVEYORS 

If coal is to be conveyed any considerable distance a belt conveyor would be used. Belt con- 
veyors will carry coal at an angle as great as 20° and may be built to handle any quantity of coal. 

The following table gives the capacity, maximum size of lumps, and advisable speed for the 
different widths of belts. 

BELT CAPACITY AND SPEED 









Capacity in Cubic 






Maximum Advis- 


Feet at the Maxi- 


Width of 


Maximum Size 


able Speed in 


mum Advisable 


Belt. 


of Pieces. 


Feet per Minute. 


Belt Speed. 


12 


2 


300 


1380 


14 


2K 


300 


1890 


16 


3 


300 


2460 


18 


4 


350 


3640 


20 


5 


350 


4480 


22 , 


6 


400 


6200 


24 


8 


400 


7400 


26 


9 


450 


9810 


28 


12 


450 


11250 


30 


14 


450 


13050 


32 


15 


500 


16500 


34 


i6 


500 


18500 


36 


18 ■ 


500 


21000 


38 


19 


550 


25300 


40 


20 


550 


28050 


42 


20 


550 


30800 


44 


22 


600 


37200 


46 


22 


600 


40800 


48 


24 


600 


44400 



When the quantity to be conveyed is small, and the pieces large, the size of the material 
fixes the width of the belt, and the speed should be as low as possible to carry safely the desired 
load. 

When the quantity is great, the capacity fixes the width, and in this case also, the speed should 
be as low as possible. A belt at slow speed may be loaded more deeply than one at high speed, 
and when a narrow belt is run much above the advisable speed, the load thins out and the capacity 
does not increase as the speed. 

The maximum length of the different widths of conveyors is determined by the fibre stress 
in the belt, and is, therefore, closely related to the load and speed. Naturally level conveyors 
may be built longer than those lifting material. Conveyors 1000 feet from centre to centre, hand- 
ling 400 tons per hour, have been most satisfactorily operated. 

Another important factor in the design of conveyors operated at high speed and handling large 
quantities is the flow of material in the chutes. A 36-inch conveyor handling 750 tons of coal per hour, 
with a belt speed of 750 feet per minute under a 10,000 ton pocket, could not be loaded from a single 
chute, because it was not possible for the coal to attain a speed of 750 feet per minute in the chute. 
It was necessary, therefore, in order to obtain a full load, to open seven gates, each placing a layer 
of coal on the belt until the desired load was obtamed. During a test this belt carried about 800 
tons per hour. 



NOTES ON POWER PLANT DESIGN 



99 



POWER REQUIRED FOR BELT CONVEYORS 

The power required to drive a belt conveyor depends on a great variety of conditions, such 
as the spacing of idlers, type of drive, thickness of belt, etc. 

In figuring the power required, it is important to remember that the belt should be run no faster 
than is required to carry the desired load. If for any reason it is necessary to increase the speed, 
the figure taken for load should be increased in proportion and the power figured accordingly. 
In other words, the power should always be figured for the full capacity at the chosen speed, as 
follows: 

C = power constant from table. 

T = load in tons per hour. 

L = length of conveyor between centres in feet. 

H = vertical height in feet that material is lifted. 

(S = belt speed in feet per minute. 

B = width of belt in inches. 



For level conveyors, 

H. P. = 

For inclined conveyors, 
H.P. 



C xT xL 
1000 



C xTxL ^TxH 



1000 



1000 



Add for each movable or fixed tripper horse-power in column 3 of table below. 

Add 20 per cent to horse-power for each conveyor under 50 feet in length. 

Add 10 per cent to horse-power for each conveyor between 50 feet and 100 feet in length. 

The above figures do not include gear friction, should the conveyor be driven by gears. 



POWER REQUIRED FOR GIVEN LOAD 





1 


2 


3 


4 






C 


C 


H.P. 








Fcr Material 


For Material 


Required for 








Weighing from 


Weighing from 


Each Movable 


Minimum 


Maximum 


Width 


25 lbs. to 75 


75 lbs. to 125 


or Fixed Tripper 


Plies of 


Plies of 


of 


lbs. per 


lbs. per 




Belt. 


Belt. 


Belt. 


Cu. ft. 


Cu. ft. 








12 


.234 


.147 


Vs 


3 


4 


14 


.226 


.143 


K 


3 


4 


16 


.220 


.140 


M 


4 


5 


18 


.209 


.138 


1 


4 


5 


20 


.205 


.136 


IM 


4 


6 


22 


.199 


.133 


1^ 


6 


6 


24 


.195 


.131 


Wi 


5 


7 


26 


.187 


.127 


2 


5 


7 


28 


.175 


.121 


2J€ 


5 


& 


30 


.167 


.117 


23^ 


6 


8 


32 


.163 


.115 


2M 


6 


9 


34 


.161 


.114 


3 


6 


10 


36 


.157 


.112 


3J4 


6 


10 



With the load and size of material known, choose from the capacity table the proper width 
of belt and proper speed. The above formulae give the horse-power required for the conveyor 
when handling the given load at the proper speed. With the horse-power and the speed known, 
the stress in the belt should be figured by the following formula in order to find the proper number 
of plies. 



100 NOTES ON POWER PLANT DESIGN 

Stress in belt in pounds per inch of width = — ^ — ~ ~ 

S X B 

With this value known, the number of plies may be determined, using 20 pounds per inch 
per ply as the maximum. Columns 4 and 5 of this table give the maximum and minimum advisable 
plies of the different widths of belt. Belts between these limits will trough properly and will be 
stiff enough to support the load. 

Belt conveyors may be driven from either end. Somewhere in the system there must be a 
tightener to allow for the stretch of the belt. The troughing idlers should be placed dependent 
upon the weight of material carried as f oUows : 

For belts 12 to 16 inches wide, from 43^2 to 5 feet apart; 
For belts 18 to 22 inches wide, from 4 to 4}^ feet apart; 
For belts 24 to 30 inches wide, from 33^ to 4 feet apart, and 
For belts 30 to 36 inches wide, from 3 to 33^ feet apart. 

The life of the belt depends a great deal upon the care which it receives, upon the material 
handled, and upon the quality of the belt to begin with. In general the life of the belt may be 
taken as from three to eight years. 

THE DARLEY CONVEYOR 

A system for handling coal or ash by a current of air flowing in a pipe has been in use in 
some plants during the last three years. A description of a system arranged for handling ash 
will show the method of operation. A pipe is laid under the floor in front of the boilers with an 
opening through the floor into the pipe in front of each ash-pit door, each opening being closed 
unless ash is being hauled from the ash-pit into it. The end of the pipe under the floor is open 
to the air. The other end of this pipe connects with a riser which leads up to the top of a closed 
steel storage tank in which the ash is to be stored. An exhaust fan or a Root exhauster draws air 
out of the tank, thus creating a flow in the pipe in front of the boilers. Any ashes, clinker, or even 
bricks dumped in through the holes in front of the boilers will be carried along by the air and 
delivered into the closed tank elevated 20 to 40 feet above the boilers. After the exhauster has 
been stopped the ashes may be discharged from this tank into a car or cart by opening an ash 
valve in the bottom. 

To quench the hot ash and to prevent dust from being drawn over into the exhauster, a jet 
of water is sent in on the ash as it is entering the closed tank. 

The fittings, especially those at the corners where the direction changes wear rapidly. The 
elbows are made with renewable chilled backs or in some cases a tee is used in place of an elbow. 
The plugged end of the tee filling up with ash causes the wear to come on the ash. 



COAL BUNKERS 

Coal bunkers may be of the cylindrical type with conical bottom ; of the parabolic type made 
either of steel plate lined or unlined with concrete or of suspended steel straps with reinforced 
concrete carryi^j.g the load between the straps, of the structural steel type carried on girders 
running either parallel with the boiler fronts or on cross girders at right angles to the boiler 
fronts; the steel being protected by a reinforced concrete lining. 

It is difficult to make a calculation of the stresses in the girders supporting a coal bunker, 
1st, on account of the unequal and variable loading and 2nd, because the coal may act like a dry 
sand under certain conditions and again under other conditions like moist earth. A treatise on 
walls, bins and grain elevators by Ketchum contains the best information available on this subject. 

The parabolic type of bunker is easy to construct and brings no eccentric load of any mag- 
nitude to the columns carrying it. 



NOTES ON POWER PLANT DESIGN 



101 



A simple method of drawing a parabolic for any sag and span is shown by the illustration. 
The actual curve is slightly different from a parabola. The coal may be heaped from the 
edges towards the centre of the span at an angle depending upon the angle of repose of coal which 
is from 35° to^40°. 

If D = the depth of the curve 
S = the span 

C = the capacity per foot of length 
X = zero at the lowest point of the curve. 



The correct equation becomes 



2D 



F = -9^ (3X2 _ 



2XA 
S J 



The capacity when filled level full is per foot of length C = .625 DS. 

The supporting forces, the thrust brought to the compression members placed between the 
columns at the top and the tension in the upper ends of the plate, may be found graphically. The 
total horizontal tension in the plate at the bottom is the same, as the total compression carried 
to the compression members at the top. 

A parabolic pocket known as the Brown is constructed of steel straps, bent to the correct 
shape, riveted at either end to channel bars attached to the columns. These straps carry the load 
and are spaced from 3 feet to 4 feet 10 inches according to the weight to be carried. On these straps 





a special crimped steel sheet known as "ferro-inclave" is laid as a reinforcing material and a 
thickness of concrete from 2" to 4" plastered over the inside and a similar but thinner coating 
on the outside. 

A section of "ferro-inclave" drawn full size is shown. 

Where the coal valves are attached, a piece of steel plate is fastened to the straps as shown 
by the illustration. 

The "Baker" suspension type has a rigid bottom carried by suspension rods spaced longitudin- 
ally at such distances as the load warrants. Between the suspension rods unit reinforced concrete 
slabs having rounded ends form the sides of the bin. The bottom may be constructed as shown 
or made up of unit slabs like the side. 

This method of constructing the sides allows of a bending of the rods, due to the loading of 
the pocket, without cracking the lining. 



102 



NOTES ON POWER PLANT DESIGN 





NOTES ON POWER PLANT DESIGN 



103 



rr- 




wk 






M 


\ 






ftm'mre, rn/^tire /.:// 


\\ 








■%v- 








¥^^N; 






/j/pJ^ 


^ 


\. 




^^^T / ^'""' ^°^™^ 


/«.. ^ . &r roy 7^1^^ SaTF 


^ 




'"i^^r / mrStcTii/n Tff" Sv'^r^"'^ Mtniet 






^/ 



Unit Concrete Slab Bin. 
"Baker" Suspension Type. 

Coal may be taken from the coal pocket overhead 
into a weighing hopper and from this discharged to 
the stoker through a spout in front of each boiler. 
The end of the spout is frequently spread out fan like 
and known as a spreader. The nozzle type is preferable 
however. 

The cut shows a spout with nozzle and with a swivel 
or universal joint at the top. The fireman by means 
of the handle directs the coal to any part of the stoker 
reservoir and fills same evenly. 

Movable weighing hoppers of capacity up to one 
ton may be installed and operated from the floor 
in plants of moderate size (see illustration). 

In large plants a motor driven crane carries a weigh- 
ing hopper of larger size which travels under the coil 
pocket over the firing aisle and automatically records 
the weight of coal fed to each stoker. 



i 



104 



NOTES ON POWER PLANT DESIGN 




NOTES ON POWER PLANT DESIGN 



10^ 



Cuts of two different weighing hoppers and a number of coal valves taken from Steam Boilers 
are given. 

Volume of Ton of Coal Cu. Ft. 

Soft coal 41 to 43 



Buckwheat or Pea 

Nut 

Furnace Size 

Coke 

Ash dry not packed 



37 
34 
36 

76 

48 to 50 






..^% 





106 



NOTES ON POWER PLANT DESIGN 



FOUNDATIONS 

CONCRETE FLOORS, WALLS, ETC. 

The type of foundation used will depend upon the character of the soil and upon the load 
to be brought to the soil. 

Baker in his Masonry Construction gives the following safe bearing loads of soils. These 
values have been generally accepted. 

Tons per sq. ft. 
Min. Max. 

Clay in thick beds always dry ...... 6 



Clay in thick beds moderately dry 
Clay soft ..... 
Gravel and coarse sand well cemented 
Sand dry, compact, well cemented 
Sand clean dry . . . . . 

Quicksand, Alluvial soils 



4 
1 
8 
4 
2 
.5 



8 
6 
2 
10 
6 
4 
1 



If the footing is spread sufficiently so that the load is carried by the soil it is customary to 
decrease the cross section of the footing as the depth decreases. 



<-o- 



<-o-^ 



With a 1-2-4 concrete the allowable offset is for a pressure on the soil of .5 ton per sq. ft 
lAt, for a load of 1 ton .8^ and for a load of 2 tons .bt where t is the thickness of the lower section 
of the footing. 

In many cases, especially where the load coming to the footing is not the same per foot, as 
for example in the setting of a water tube boiler, it is customary to reinforce the footing with steel 
rods or with steel beams buried in the concrete. 

If the land on which the structure is to be built, is made land, it will probably be necessary 
to put in piles to support the footing. 

The piles may be either wooden or concrete. The wooden piles cost for oak 20 to 30 feet 
long 6" top 12" butt 17 cents per foot of length; oak 40 to 60 feet long, 21 to 25 cents per foot of 
length; spruce, 20 to 30 feet 15 cents per foot of length. 

The cost of driving a pile and cutting off is about 9 cents a foot. 

Concrete piles cost about $20 for a 40 foot length as against $9.50 for wooden piles; the bear- 
ing power of a concrete pile is however 2.5 times that of a wooden pile. 

Wooden piles should not be driven closer than 30" on centers. 

The safe bearing load of a wooden pile may be figured with more or less uncertainty by what 
is known as the Wellington or the Engineering News formula: 

P = safe load in lbs. (factor of six used) 
M = weight of drop hammer in lbs. 

h = fall of hammer in ft. 

s = penetration or sinking in inches at last blow. This to be measured when there is 
no appreciable rebound of the hammer and the head of the pile is not broomed. 



NOTES ON POWER PLANT DESIGN 



107 



If there is a rebound the drop of hammer should be reduced. 

2Mh 



P = 



s + 1 



Illustration 



Hammer = 3000 lbs. 
Drop in ft. = 10 
Penetration = 3" 



P = 15,000 lbs. 



BRICKS 

A mason and laborer will lay 1000 to 1500 bricks per day in a wall averaging 10" to 12" thick. 
The cost of labor per 1000 bricks laid, including mason and helper and cost of erecting stagings 
is from $8.00 to $8.50. 

Bricks cost from $7.50 to $10.00 per 1000 and a thousand bricks will lay about 2 cubic yards 
of masonry. 

It takes about 20 bricks 83^" x 4" x 23^" per cubic foot; the masonry weighing 125 lbs. per 
cu. ft. 

In a power house the floors are usually of reinforced concrete on steel beams. The boiler room 
floor is generally figured for 250 lbs. live load and the engine or turbine room for 400 lbs. live load. 

The dead load of various types of floors may be estimated from the following approximate data : 
the weights are given per sq. ft. of surface. 



Wooden wearing surface 
Granolithic finish 
Cinder filling 
Stone concrete . 
Cinder concrete 
Plaster, 2 coats 



4 lbs. per inch thick 
12 lbs. per inch thick 

5 lbs. per inch thick 
123/^ lbs. per inch thick 

9 lbs. per inch thick 
5 lbs. per inch thick 



The dead load of any roof may be estimated from the following 

5 ply felt and gravel roofing 
3 ply ready roofing 
Slate 3/16 thick 
Clay tile 
Tin roofing 
Copper roofing . 
Corrogated iron 
Dry cinders 



6 lbs. 
lib. 
73^ lbs. 
12 lbs. 
lib. 

2 lbs. 

3 lbs. 

4 lbs. 



The minimum live loads, for roofs pitching less than 20° vary from 30 to 50 lbs. per sq. ft. 
according to different City Bldg. Laws. 

For a pitch greater than 20°, 25 to 30 lbs. should be used. 

For light floor loads a 1-3-6 concrete might be used. This mixture might also be used in 
walls carrying but small loads. For heavy loads or for columns a 1-2-4 or richer mixture would be 
used. 



108 NOTES ON POWER PLANT DESIGN 



REINFORCED CONCRETE FLOORS 

Various types of reinforcing rods, woven wire fabric, welded wire fabric and expanded metal 
are used as reinforcing material in concrete floors. The woven fabrics and the expanded metal 
are made in certain definite sections and from tests which have been made on slabs of different thick- 
ness, the makers of the various reinforcing fabrics have constructed tables some of which have 
been given in these pages. 

While tables might have been given for the strength of slabs reinforced by rods of one type 
or another, it was felt that one had better make his own calculations for such cases. 

The formulae generally given for figuring reinforced concrete beams and slabs are derived on 
the assumption that (1) the tensile resistance of the concrete may be neglected and (2) that the 
stress diagram for the concrete is a straight line up to the safe compressive strength of the concrete. 

The formulae and notation given below are practically as given in Turneaure and Maurer's 
Principles of Reinforced Concrete Construction. See also Baker's Treatise on Masonry Construc- 
tion, Report of Joint Committees of Engineering Societies and Taylor & Thompson's Reinforced 
Concrete. 

fs = fibre stress in steel per sq. inch taken as 16 to 18,000 lbs. 

fc = fibre stress in concrete, the maxinjum compression per square inchi at outer face; for 1-2-4 

stone concrete from 600 to 700 lbs. ; for 1-2-4 cinder concrete from 300 to 400 lbs. 
Es = elongation of steel per inch of length due to stress fs per sq. inch. 
Ec = shortenmg per inch of leng-th of the concrete due to the stress /c per sq. inch. 
Es ?= modulus of elasticity of steel. 
Ec = modulus of elasticity of concrete in compression. 

pi 
n = r~f generally taken as 15 for 1-2-4 stone concrete and as 30 for 1-2-4 cinder concrete. 

Ec 

T = total tension in the steel at any section of the beam. 
C = total compression in the concrete at any section. 
Ms = resisting moment as determined by the steel ; inch lbs. 
Mc = resisting moment as determined by the concrete; inch lbs. 
M = bending moment or resisting moment in general; inch lbs. 
h = breadth of rectangular beam or slab in inches. 

d = distance in inches from the compressive face of the concrete to the plane of the steel. 
K = ratio of the depth of the neutral axis of a section below the top, to the distance d, generally 

taken as .375. 
j = ratio of the arm of the resisting couple to the distance d. 
A = area of cross section of the steel. 

P = — — = the steel ratio generally from .007 for a 1-2-4 cinder concrete to .0122 for a 1-2-4 
stone concrete. 

Since cross sections that were plane before bending remain plane after bending the unit defor- 
mations of the fibres vary as their distances from the neutral axis. 

■p fc 



Es 
Ec " 


d-Kd 
' Kd 








Ec Es fc fc 


d-Kd 

~ Kd 


-K 

K 



NOTES ON POWER PLANT DESIGN 



IOC 



as the total tension equals the total compression 
f,Pbd=y2fcbdK; 



P=V2K 



but j^ = n ^-^- 



u — n K 
K 



P=V2K 



K^ + 2 Pn K + {PnY = 2 Pn + {Pn)'' 
K + Pn= V2Pn + {PnY 



Es 



from which K may be found as soon as the steel ratio is known and the ratio of -^ 




j d= d - HKd 
If K = 0.375 



j =1 - VsK 

j = 0.872 or about % 



A value of j = .85 is used by some designers on both cinder and stone concrete of 1 -2-4 mixture 

Ms=Tjd = fsAjd = fsPjbd^ 
Mo=Cjd=y2fcbKdjd=y2foKjbd' 

The fibre stress in the steel for a given bending moment is equal to 



/. 



M 



M 



Ajd Pjbd^ 



The fibre stress in the concrete /c = ^j^-j^ equating values of M; 



2M_ 

Kjbd^ 



fc = 



2fsP 
K 



bd^ 



2M 

fcKj ' 



bd^ = 



M 

fsPj 



110 NOTES ON POWER PLANT DESIGN 

W l^ 
The bending moment for beams and for slabs contmuous over the supports is M = — -— , where W 

is the load per inch of length and / is the length in inches. If continuous over one support only 

W l^ W P 

M = - - ;" while if freely supported M = — — 

If a rectangular slab be reinforced in two directions the bending moment would, for a square 

W l^ 
panel where one-half the load would be carried in each direction, be ikf = , where W is the 

total load per square inch. 

For a rectangular panel the proportion of the load carried by the reinforcement placed the 

short way of the span is r = -^ — p 

rW P 
The reinforcement for the short span is then figured taking as the bending moment 



and in a similar way the reinforcement for the long span by using a value of ikf = 



10 

{\-r)W P 
10 



The distance from the center of the reinforcing bars to the bottom of the floor slab should be 
1"; the distance between centers of adjacent bars at least 23/^ diameters. 

The distance from the side of a beam or slab to the center of the outer bar should be about 
2 diameters of bar. 

The bearing pressure per square inch where a slab rests on its supports is not to exceed 650 
lbs. per sq. inch. 

Concrete beams sometimes fail through diagonal tension; floor slabs seldom fail in this way. 
A beam or slab may be made safe against such failure by keeping the average shear on a concrete 
having a compressive strength at 28 days of 2000 lbs., under 40 lbs. per sq. in. in cases where the 
horizontal reinforcing steel is not bent so as to offer help in resisting diagonal tension: where the 
reinforcing material is bent so that it does offer help the average shear may be taken as 60 lbs. 
per sq. in.; where ample reinforcement for resisting diagonal tension is specially provided, the 
average shear in the concrete may be taken as 120 lbs. per sq. in. 

As the horizontal and the vertical shear are of the same intensity, the unit shear may be 

, Vertical shear on Section 
expressed as = r-^ 

j may be taken as .85 or .87. 

In finding the area of reinforcing steel (As) necessary for width 6 if it be assumed that the 
concrete resist one third of the total shear (F) on this width, and the steel the remaining two- 
thirds, then for vertical stirrups spaced a distance (*S) apart longitudinally 

A - ^^^ 

If the reinforcing material makes an angle of 45" "then the area of the steel becomes .7 of this 
value. 

If the safe bonding strength of steel rods be taken as 80 lbs. per sq. inch of rod surface, and as 
40 lbs. per sq. inch of wire surface then calling (o) the entire surface per inch of length of rods in 

V 
a section Cb) the bond stress per unit of surface of the bars = . , which must be less than 80 for 

■ jdo 

rods and less than 40 for wire. 



NOTES ON POWER PLANT DESIGN 



111 



Example : 

A continuous slab 8'-4" span is to carry a total load of 288 lbs. per sq. ft. — the slab to be 
of 1-2-4 stone concrete. Required depth of slab and area of reinforcement. 

/c = 650 lbs. sq. inch. 
fs = 16,000 lbs. sq. inch. 
n= 15 

288 X 100 X 100 

= 20,000 



r ui SI 


iiiy L 


/J WlUC IV. 


L — 


12 X 12 


bd^ = 




40,000 




188 


650 


X .375 X 


.872 


P = 




20,000 




= .762% 


188 


X 16,000 


X .872 


d' = 


188 


= 15.66 


d 


= 3.96" 



12 

use 5" slab. 

Steel 4 X 12 X .00762 = .366 sq. ins. per ft. width 
use 5^" rods spaced 3" on centres. 

1200 



The unit shear = 
The bond stress 



12 X .87 X 4 

1200 



29 lbs. 



.87 X 4 X (4 X .375 x tt) 



= 74 lbs. 



Some types of concrete floors are shown by illustrations taken from the Catalogue of the 
Clinton Wire Cloth Co., Clinton, Mass. The wire cloth consists of a wire mesh made up of a 
series of parallel longitudinal wires spaced certain distances apart and held at intervals by means 
of transverse wires arranged at right angles to the longitudinal ones and electrically welded to 
them at the points of intersection. 

A regulation governing the use of any type of reinforcement for concrete floors in New York 
City requires that the system be subjected to a load test. The test is made upon a sample floor 
approximating as nearly as possible the conditions of actual construction, and the particular span, 
slab and reinforcement as tested are approved by the Bureau of Buildings for one-tenth of the 
load which the test specimen actually carries. 

The following floor slabs have thus been tested in New York City and approved by the Bureau 
of Buildings for the various live loads as given: 

The dias, of wire correspondmg to W. & M. gages: 





dia. 


area 


No. 3 


.331 


.086 


No. 4 • 


.307 


.074 


No. 5 


.283 


.063 


No. 6 


.263 


.054 





dia. 


area 


No. 7 


.244 


.047 


No. 8 


.225 


.040 


No. 9 


.207 


.034 


No. 10 


.192 


.029 



In this type of reinforcement the wire is placed %" above the bottom of the slab on all slabs 
from 3" to through 43^" in thickness; 1" above on thicknesses of 5", 6" and 7"; and 134" above 
on slabs 8" thick. 

Another reinforcing material known as "steelcrete" made by the Eastern Expanded Metal 
Co. of Boston is shown by the illustration which appears on page 114. 



112 



NOTES ON POWER PLANT DESIGN 



•^- 




■ -.V ■ U« ■ -i •* 4 



"^A'U /£' Afesfy *7-^/0 C///7/-0/? M/^e<^ Mre 



C///)fo/7 JY^/(^ec/ )y/'re 




7'-6' 



Approved L.ive Load 200 Pounds Per Square Foot 




r-^ 



l-Z'S C/nc/er Ca/?crefe 



----- ■■ "u 'J >■■' ■ -I ■ 

^^'x/2'Me5/? *J~9 C///?fa/7 Jrl'/a'^i/ Mre 



Approved Live Load 250 Pounds Per Square Foot 








Z"x8"Me5/7 *3'd C//nf£>/7 )fe/ded hire 



Approved Live Load 150 Pounds Per Square Foot 

/■ 1-2-^ C//?der Concrete 




^d'x /a" Afes/? ^S-/0 C//nton }fe/<:/ec/ JiT/re 
6'-D" 



\ V 




Approved Live Load 150 Pounds Per Square Foot 



^ 



/-E-ff 0/7der Ca/?cre/s 



:r^J 




t: 



a^ 



" ■■ ' '-' ■ "^"' -" 



-■^'x/tMes/? *J-*3 Cf/ntan Jfe/ded M're 



^t-C//>7Ap/7 M/dec/ Mrt^ 



6'-6 " 




Approved Live Load 300 Pounds Per Square Foot 



rfi 



1-2-S C/nder Co/?crefe 





•3'xl2" MesA *4^9 C///?fo/J /fe/dea^ Mre 



(J-6' 



C/into/? //e/ded J//re 



Approved Live Load 400 Pounds Per Square Foot 



NOTES ON POWER PLANT DESIGN 



113 



This cut also gives some idea of the method by which the mesh is manufactured. 

"Steelcrete" can be obtained in lengths up to 144" and in lengths less than 144" varying by- 
some multiple of 8". 

The size of the diamond, weight of reinforcement per sq.ft., etc., are given in the following 
table which has been taken from the maker's catalogue. 




DECIMAL STANDARDS FOR "STEELCRETE" EXPANDED METAL 





Width of 


Length of 


Section in 


Wt. per 


Number Size of Standard 


Number of 


Wt. per 




Diamond 


Diamond 


sq. in. per 


square foot 


of Sheets 


Sheets 


sq. ft. in 


bundle in 








ft. of width 


in lbs. 


in a bundle 




a bundle 


lbs. 


Designation 


of Size of Mesh 














Mesh 


















3-13-075 


3" 


8" 


.075 


.27 


10 1 


r6'0"x 8'0" 
1 6'0" x 12'0" 


480 
720 


129.6* 
194.4 


3-13-10 


3" 


8" 


.10 


.37 


7 1 


r6'9"x S'O" 
1 6'9" X 12'0" 


378 
567 


' 139.9 
209. S 


3-13-125 


3" 


8" 


.125 


.46 


7 1 


r5'3"x 8'0" 
[ 5'3" X 12'0" 


294 
441 


135.2 
202.9 


3-9-15 


3" 


8" 


.15 


.55 


5 , 


r7'0"x 8'0" 
1 7'0" X 12'0" 


280 
420 


154.0 
231.0 


3-9-20 


3" 


8" 


.20 


.73 


5 ^ 


f5'3"x 8'0" 
1 5'3" X 12'0" 


210 
315 


153.3 
230.0 


3-9-25 


3" 


8" 


.25 


.92 


5 ' 


r4'0"x 8'0" 
1 4'0" X 12'0" 


160 
240 


147.2 
220. S 


3-9-30 


3" 


8" 


.30 


1.10 


.2 1 


r7'0"x S'O" 
1 7'0" x 12'0" 


112 

168 


123.2 
184.8 


3-9-35 


3" 


8" 


.35 


1.28 


2 1 


r6'0"x S'O" 
1 6'0" X 12'0" 


96 
144 


122.9 
1S4.3 


3-6-40 


3" 


8" 


.40 


1.46 


2 1 


r7'0"x S'O" 
7'0" X 12'0" 


112 

168 


163.5 
245.3 


3-6^5 


3" 


8" 


.45 


1.65 


2 1 


^6'3"x S'O" 
6'3" X 12'0" 


100 
150 


165.0 
247.5 


3-6-50 


3" 


8" 


.50 


1.83 


2 1 


'5'9"x S'O" 
5'9" X 12'0" 


92 
138 


168.4 
252.5 


3-6-55 


3" 


8" 


.55 


2.01 


2 1 


^5'3"x S'O" 
5'3" X 12'0" 


84 
126 


168.8 
253.3 


3-6-60 


3" 


8" 


.60 


2.19 


2 1 


'4'9"x S'O" 
4'9" X 12'0" 


76 
114 


166,4 
249.7 


3-6-75 


3" 


8" 


.75 


2.74 


2 1 


'3'9"x S'O" 
3'9" X 12'0" 


60 
90 


164.4 
246.6 


3-6-100 


3" 


8" 


1.00 


3.66 


2 1 


'2'9"x S'O" 
. 2'9" X 12'0" 


44 
66 


161.0 
241.6 








"STEELCRETE" SPECLA.L MESHE 


S 






^-13-25 


.95" 


2" 


.225 


.80 


5 


6'0" X S'O" 


240 


192.0 


13^-13-20 


1.36" 


3" 


.181 


.73 


5 


4'0" X S'O" 


240 


116.8 


2-13-15 


1.82" 


4" 


.15 


.50 


5 


S'O" X S'O" 


200 


100.0 



114 



NOTES ON POWER PLANT DESIGN 





"St€®!cir<tt@ Mesh Slab TXbles 

-Tor use with 

Gravel or Stone: CoNCReTE:. 






Maximum 5tress in 5+eel = l8,50O lbs. per sc^. inch. 
Maximum5+re3s in Concrete = 750 lbs. per scj^. inch. 

Maximum Bending Monnen-|- = M = TSvvl*. 
where 

sr-\o\a\ load per sc}.. j-T. 
1 =cen+er +o cen+er span. 




3-/3-07S"5f<fe'/c/-ei'e'£-x/>one/ea''Afe'/a/. Area -^ O.07S S^./^. per /?. of *y/'<yM. 


U/7/f S/'ress ej 
7J)S. per sif- '/>■ 


/' 


S/>a/j- 1 


'f-0~ 


■9-<i' 


-5--0- 


-5--<S" 


6-0" 


6-6' 


7-0' 


7-6- 


8-0' 


9-0- 








Co/>cre/£ 


<S/-<:e/. 


3* 


/43 


/OS 


78 


S8 


-^3 


3/ 


22 














4SS 


/3,soo 


3-^ 


/78 


/^/ 


98 


73 


3S 


40 


29 


/9 












4oS 


" 


^ 


Z/4 


/S8 


//9 


89 


67 


So 


36 


2S- 












370 


" 


'^■^ 


ZSO 


/ss 


/4o 


/o6 \ 8o 


40 


44 


3/ 


20 








34a 





S 


286 


Z/3 


76/ 


/2Z 


93 


70 


^2 


37 


2S 










3ZS 


* 


& 


S"^? 


Zi,(, 


20/ 


/-53 


//7 


89 


^6 


4S 


33 










2 90 


♦ 


7 


429 


32/ 


243 


786 


/■4'2 


/09 


82 


^0 


42 


/S 








260 '■ 1 


8 


Joo 


374 


23'f 


2/S 


767 


/27 


94 


7/ 


So 


/9 








Z40 


" 


9 


^74 


430 


327 


23/ 


793 


/■^3 


//2 


S3 


60 


24 








ZZ/? 


ti 


/o 


^■ad 


43^* 


369 


283 


Z/8 1 767 


/27 


94 


68 


27 








2/0 


" 


// 


7/9 


S39 


4// 


3/6 


24^^ 


787 


/43 


/07 


77 


3Z 








Zoo ' 


-/z" 


792 


S94 


433 


348 


269 


207 


/S8 


7/S 


8S 


36 








/9o 


y-/3-/0 t5^ee/cre/e ' ^xpa/fi/ca' /^eT't^/. y^re^r - /P./a4> J^. //^/ter/y. £>/' iv/i/f'A. 


/6s.per s^./n- 


/■ 


^pan. 


4-o' 


4-6' 


S-o- 


^-6' 


^=-0" 


6-6' 


7-0' 


7-6- 


S-o" 


9-o' 


/a-o" 






Co/tcre^ 


c5/ffe/ 


3' 


ZO/ 


/S/ 


//S 


89 


69 


^3 


4/ 


3/ 


23 










S4o 


/3.S00 


3-k 


£■^9 


/88 


/44 


/// 


86 


67 


^Z 


39 


29 . 










48a 


» 


4 


Z98 


2ZS 


7 73 


734 


/OS 


82 


6'tl 


49 


37 


/9 








43S 


■■ 


4^ 


34^8 


263 


203 


/3S 


/2^ 


97 


76 


■^9 


43^ 


24 








400 


' 


S 


SfS' 


3oZ 


232 


78/ 


7^2 


/72 


38 


69 


S3 


29 








37S 


' 


6 


49d 


376 


290 


227 


/79 


74/ 


7/2 


87 


6S 


38 








330 


1 


7 


S97 


433 


3S/ 


273 


2/ 7 


772 


734 


/07 


S4 


48 


22 






3oS 


- 


8 


697 


^Jo 


4/0 


32/ 


2S^ 


Z02 


76o 


/27 


99^ 


37 


27 






28o 


" 


^ 


798 


6o7 


47o 


369 


292 


232 


/8S 


/47 


//S 


^S 


34 






26 


" 


/O 


89i, 


682 


S29 


■^/3- 


329 


262 


209 


/as 


/3o 


77 


3S 






24S 


. 


// 


99S 


76/ 


S9o 


-464 


368 


293 


234 


/36 


/47 


87 


4S 






23o 


* 


/z- 


/09S 


836 


6SO 


^/o 


4oS 


323 


2S3 


2oS 


/6 2 


97 


so 






22 


H 


3-/3- /ZS "<5fe-e'/crtf/e" ^Xyoa/ya'ee/ />^e-Ay/. ^re'a =a./Z^s^. /h/^er-/'/: of ^y/^/^ 


U/z/V-ti^/^resses 
/Sspe/- 39. /h- 


»>•"■ 


<5po/7. 


^-o' 


'^-6" 


3-o' 


3-6 " 


6-0- 


6-6' 


7-o~ 


7-6' 


3-0' 


9-o' 


/o-o' 


//-o " 


/2^o' 


Co/ycre-/^ 


S/'e^/ 


3' 


ZS8 


/9^ 


/S2 


7/9 


94 


7S 


S9 


47 


37 


2/ 








d/O 


/8,SOO 


3i 


3/9 


2^3 


733 


/48 


//7 


94 


7S 


S9 


47 


28 








34s 


" 


4 


382 


Z9/ 


2Z6 


/73 


/42 


7/3 


9/ 


73 


S3 


3S 


/9 






49o 


" 


4-k 


44S 


S^^o 


26S 


ZOf 


/67 


73-^ 


/08 


86 


£9 


43 


24 






4SS 


A 


^ 


So8 


383 


303 


240 


/9/ 


7S4 


/24 


/oo 


Sa 


s/ 


29 






42S 


' 


^ 


d3S 


486 


379 


300 


2-ao 


794 


/37 


/27 


/o2 


6S 


39 


/9 




380 


i> 


7 


7iZ 


^84 


4S7 


362 


29o 


234 


/9o 


7SS 


/2S 


8/ 


49 


2S 




34S 





8 


889 


68/ 


333 


423 


3-^0 


27S- 


223 


78/ 


/47 


96 


Sff 


37 




320 


" 


9 


/0/8 


782 


6/2 


486 


39o 


3/6 


237 


2/0 


/7/ 


/// 


69 


37 




300 


« 


/o 


//4S 


878 


688 


S47 


440 


3S6 


290 


23(1, 


/93 


726 


73 


43 


76. 


27S 


/f 


// 


/Z7S 


979 


767 


6/0 


49/ 


398 


324 


26S 


2/6 


742 


S9 


So 


20 


26S 


" 


/z- 


/4oi 


/076 


844 


672 


34/ 


438 


3S7 


292 


23S 


/S7 


99 


SS 


23 


2So 


ft 



NOTES ON POWER PLANT DESIGN 



115 



























































1 


3 


■^-0' 
J/4 


s '5 

Z40 


/ee/cr 

3-0' 

/87_\ 


■e/e" J. 

3-6" 
748 


^x/>a/ 

6-0' 
779 


^'-6' 
9'6 


7Ve/^ 

7-0' 
7Z 


7/. A re<7 = a. ^3a 3f 
<5pan 

7-6" 8-0' 9-o~ /o-o' 
63 37 32 7^_ 


//J./>e/'/^>^ 
77-0" 7Z-6 


of yy/a^/^- 

/3-0 




d//7//^fre35es. 

/J,3. fie/- 3if . //? 

Concre/e c5"/<?«»/ 

6.7S 78SOO 


j4 


3S9 


Z9S 

3S7 

4.7/i 


Z3S 
Z7f 
3Z<i 
37'4 


783 
ZZZ 
Z6o 
Z98 


7^8 
/79 
^o^ 
847 


/■43 
770 
79<6 


97 
778 
73^ 
76o 


79 
96 
//'4 
732 


^4 
79 

/OS 


32 
62 
72 


Z3 
32 
■40 


23 
^8 











S3o 
3^os 
47a 


' 


^ 


77/ 


.■f*^ 


'fiZ 


373 


30/ 


Z43 


Zo/ 


766 


737 


9Z 


160 


37 


79 








^20 


* 


■7 


9 7" 7 


7/S 


3^Z 


^49 


364 


297 


244 


202 


767 


7/3 


7S 


47 


26 








S80 


" 


o 


/OS/ 


8J4 


£3^ 


3ZS 


4/23 


348 


Z86 


23^ 


793 


733 


89' 


3^ 


37 








33-0 


" 


o 




^^■a 


73Z 


6>oZ 


483 


399 


329 


Z7Z 


ZZ3 


733 


/04^ 


66. 


38 








330 


'/ 


7 


/394 


/07^ 


847 


67S 


33t3 


4So 


377 


J07 


233 


773 _ 


778 


7ti 


■44 


^f 






30S- 


" 


// 


/3SO 


7/97 


9^3 


736 


6/3 


3o3 


■4/^ 


343 


Z83 


797 


733 


36 


37 


23 






2^90 


• 


/Z" 


/7£>S 


/3/^ 


/OST 


332 


67S 


333 


436 


37S 


3/4! 


2/7 


7^7 


93 


36 


26 \ 






273 


" 


3-9-ZO 'Si^'^e/cre'j^e'^X/Jo^c/ea'/Ve/'ij/. y^fera = a. Zoo s^. /n.pe,^/?. of tv/c/^h- 


6//>//^ S/r esses 
/6s.joe/- Sit- //">■ 


i«b 


<5/3on. 


^\''' 


^■-0" 


^^^-- 


£-0" 


3-6- 


6-0" 


<6-6- 


7''0" 


7-6" 


8-0" 


9-0" 


70-0' 


7/-0 


' 72-0- 


/3-0 


74-a 


73-0" 


Co/fcre/^ 


S/e.e7 




397 


30^ 


24/ 


793 


736 


/Z3 


703 


87 


72 


■49 


33 


20 










7SO 


77400 


3± 


SZ.S' 


4a4, 


3SO 


2S7 


Z09 


77/ 


/■^Z 


7/8 


98 


68 


47 


37 


79 








7/0 


78. 3 00 


4. 


£ZS 


48i 


38^ 


309 


237 


^07 


777 


743 


7ZO 


84 


38 


40 


23- 








643 


" 


4i 


73/ 


sa 


448 


360 


294 


242 


ZO/ 


768 


747 


/oo 


7a 


48 


32 


79 






393 


" 


s 


836 


^47 


s/z 


4/3 


337 


Z78 


237 


793 


762 


/73 


82' 


37 


38 


Z3 






333 


" 


<i 


/04/ 


SOS 


64o 


3/6 


42/ 


348 


Z9o 


243 


2o4 


746 


7o4 


73 


49 


3/ 






49 


" 


7 


/ZS/ 


970 


770 


62/ 


3o3 


^Zo 


330 


Z94 


248 


777 


/Z7 


9o 


62 


40 


Z2 




443 


" 


s 


/■ai/ 


//S3 


399 


726 


394 


49/ 


4/0 


344 


29o 


~; 


'OS 


/30 


706 


73 


48 


27 




4/0 


" 


9 


/i,7/ 


/Z97 


/OSO 


832 


68/ 


3^4 


47Q_ 


39^ 


334 


'4/ 


773 


724 


86 


37 


34^ 




380 


" 


/a 


/880 


/4iia 


7/39 


936 


767 


633 


330 


4^46 


.372^ 


Z77 


79<& 


740 


^8 


63 


39 


78 


360 


■' 


// 


Z093 


7^24 


/ZS9 


/t>42 


834 


707 


39/ 


-997 


■42/ 


3o4 


220 


733 


7/7 


74 


43 


22 


340 


♦ 


/z" 


Z30Z 


7788 


74ZO 


//47 


940 


779 


63/ 


348 


•^63 


333 


242 


774 


7Z3 


8Z 


3^0 


24 


3ZO 


" 


3- 9-SS '<5fee/cre/^ ^x/>0r>^ea' /V<s'/o/ /lr<fa = ^.^sa s^. //7./>e/-/7. of tv/e//A. 


On// (5//'e3ses 
/6s. per 3<f. /7) 


,/■ 


^pa/7 


^-0' 


■4-6' 


3-0 


J-6 


6-0" 


6-6- 


7-0' 


7-6' 


8-0' 


9-8- 


70^0' 


/7-0' 


/Z-o' 


/3'0 


/4-6 


/3-0 


76-3' 


/7-0 


' /S-o' 


Co/)cre/e 


S/ee/ 


3- 


4Z8 


330 


86/ 


Z09 


/70 


739 


7/3 


93 


79 


33 


37 


24 
















730 


7S/00 


3-k 


ias 


47/ 


373 


30/ 


Z46 


Z03 


769 


74/ 


7/9 


83 


60 


4Z 


Z8 














" 


/7,Zoo 


4 


787 


6./Z 


486 


393 


3ZZ 


Z67 


ZZ3 


/88 


/39 


7/3 


34 


6/ 


43 


29 


78 










730 


7 8, 300 


4-k 


f/i 


7/Z 


366 


438 


376 


3/Z 


Z6Z 


ZZ/ 


787 


736 


700 


73 


3Z 


36 


Z3 










£7S 


» 


s 


/o4S 


8/6 


649 


3Z6 


43/ 


338 


30/ 


Z34 


Z/6 


787 


776 


83 


6/ 


43 


29 










630 




i, 


/309 


/0/9 


8// 


637 


340 


449 


377 


3/9 


27/ 


798 


746 


/08 


79 


36 


38 


Z3 








36o 


" 


7 


/S7/ 


/ZZ3 


974 


790 


63o 


34/ 


433 


383 


3Z8 


Z4/ 


778 


/3Z 


97 


70 


48 


3/ 


/7 






3o3 


" 


8 


/634- 


/4Z8 


7/37 


9Z3 


7&0 


63Z 


33/ 


450 


384 


Z8Z 


Zo9 


/S6 


7/3 


83 


38 


38 


Z/ 






.460 


" 


f 


2099 


7637 


7304 


7038 


87Z 


7Z6 


6/0 


3/8 


44/ 


3Z3 


Z4Z 


/e/ 


/34 


98 


69 


43 


Z6 






430 


• 


/o 


Z3i,4- 


/S40 


/4i7 


//f/ 


'fSo 


8/7 


687 


383 


497 


366 


273 


Z04 


73/ 


/// 


78 


32 


30 






4o3 


" 


// 


Zi3/ 


Zo3/ 


7633 


73ZS 


/o9Z 


9/0 


766 


649 


33S 


409 


303 


ZZ9 


/7o 


/zs 


89 


60 


36 






383 


ft 


/z" 


ZSfg 


ZZS8 


/eoo 


7467 


7Z03 


/ao4 


f 843 


7/7 


6/Z 


43Z 


338 


Z33 


769 


738 


99 


/7 


40 


M 




360 


" 


3- f-3o ^/ee/c/-e^c " ,<£^v^^/7,^i"^y%'/^/ /^n^a = a.300 s<f. //} ./>&/- /)i ofpr/iZ/A. 


//o// (S/ress&s 
/^s.joej- S9. //}■ 


,.» 


<5/)a/>. 


'^-O' 


41-6- 


^-0" 


^-ti' 


^-0" 


6-6' 


7-o' 


7-S" 


8-0' 


9-0' 


70-0' 


77-0 


' 7Z-o' 


73-0' 


/4-0' 


/3-0' 


76-/>' 


/7-0 


' 78-0' 


Co/?cre/e 


c5-/.r^/ 


3° 


4Si. 


333 


Z79 


ZZ4 


78Z 


/30 


784 


703 


M 


6/ 


■4Z 


28 
















730 


73!,3oo 


3-k 


64S 


£00 


397 


3ZO 


Z6Z 


Z/7 


/e/ 


/3Z 


/zg 


9Z 


66 


47 


33 














« 


/S,3oo 


4- 


8£i 


674 


336 


433 


337 


Z97 


Z49 


Z// 


/79 


73/ 


97 


77 


3Z 


37 


ZS 










„ 


/7,aoo 


4i 


//OZ 


838 


683 


336 


438 


38Z 


3ZZ 


Z73 


233 


/73 


729 


97 


73 


34 


39 


Z6 








1. 


78,300 


S 


/ZS? 


98Z 


784 


637 


3Z6 


438 


869 


3/4 


Z69 


/t4 


/44 


//3 


83 


63 


46 


3Z 


Z/ 






70/) 


« 


& 


7374 


/ZZ7 


f8o 


797 


638 


349 


463 


394 


137 


25/ 


/89 


743 


708 


8/ 


60 


4Z 


28 






6Z0 


■' 


7 


789/ 


7473 


7/79 


939 


79Z 


662 


339 


473 


408 


304 


ZZ9 


/74 


733 


/OO 


74 


34 


37 


;?? 




36o 


-/ 


.8 


ZZOS 


/rzi 


7378 


///9 


9Z4 


773 


633 


3S6 


476 


333 


Z69 


Zos 


- 736 


7/8 


88 


64 


44 


Z8 




3/3 


-, 


f 


ZSZh 


/970 


/376 


/283 


/060 


886 


749 


638 


347 


409 


3/0 


Z37 


78/ 


738 


703 


76 


33 


34 




473- 


.. 


/o 


zefz 


22/7 


/774 


/444 


7793 


998 


844 


779 


6/7 


46/ 


330 


Z67 


Z03 


736 


//7 


86 


60 


39 


ZZ 


■443 


* 


// 


3/i3 


Z47Z 


/974 


76o8 


/3Z9 


///3 


94/ 


80Z 


688 


3/3 


39/ 


Z99 


Z30 


773 


/3Z 


98 


69 


46 


z6 


4Zo 


'/ 


/2' 


3488 


Z7ZZ 


Z/79 


InzL 


7466 


/ZZi 


//>37 


884 


73f 


368 


43Z 


3?/ 


Z54 


794 


747 


7/>9 


77 


3/ 


30 


400. 


ti 



116 



NOTES ON POWER PLANT DESIGN 



...... -" ■ ■,..■,.■ ■ j.-^TTr?^— .^ . 1 1 . — 

:3-'f-3S 'Sfee/cre/^' j^^yDa>/?^et//Ve'/a/. Area" a.3Sff s^. /n.y^ef /?. o/ ^v/^//^ 


//n/T-tSfresses. 


i/ib 


^/san- 1 


76s. per 3f. //?■ 


^' - 


4-o' ■ 


««-<«' 


s-o' 


3-i' 


<i-0 


^-^'- 


7-a 


7-^' 


3-0 


9-0' 


/o-o' 


//-a' 


/2-0' 


/3-0' 


/4-0 


/3-0' 


/6-0' 


/7-0 


/8-8 Concrere\ 


S/ee7 


3° 


4S0 


372 


294 


236 


793 


739 


732 


7/0 


92 


43 


44 


3/ 


20 














V30 


7ZZO0 


^ir 


6SZ 


3Z7 


4ZO 


340 


Z7/f 


23/ 


793 


762 


/37 


99 


72 


32 


37 


23 












" 


78. 9oo 


4 


9/^fi 


7t}7 


.S^3 


4S7 


37^ 


3/3 


Zi.3 


22Z 


/fo 


/39 


/03 


77 


34 


4/ 


28 










ft 


/S.400 


U 


//^{. 


9/0 


7Zi. 


.f9fl 


488 


4/>7 


343 


292 


2SO 


/8S 


/4o 


70 & 


80 


40 


44 


3/ 


20 






« 


76, 9oo 


S 


/^44 


//Z'T 


9o3 


77<f 


/,08 


3o9 


430 


3^7 


3/3 


234 


/79 


/37 


704 


8/ 


4/ 


43 


32 


22 




" 


78, 2 00 


6 


/83.'! 


7434 


//4S 


93^ 


77S 


/i49 


■349 


44-9 


403 


30Z 


23/ 


/78 


/37 


/o4 


8/ 


4/ 


44 


3/ 


/9 


47S 


78.300 


7 


Z203 


/7Z3 


/379 


//23 


93/ 


78/ 


&&/ 


343 


48i 


344 


28o 


2/6 


748 


/30 


/oo 


74 


34 


40 


24 


470 


m 


8 


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118 



NOTES ON POWER PLANT DESIGN 





"Steskmtl lESH SlAB^XBLES 

for use with 






Maximurin Stress m Steel = 16,000 lbs. per sq. Inch- 
Max'imurn Stress in Concrete=300lbs.per* sq. inch , 

Maximum Bending Moment = M = is wt^ . 
where 

w- = totcil load per scj.. ft. 
1= center* +o center span. 




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/As /}er S^. /h. 


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NOTES ON POWER PLANT DESIGN 



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c^/^e/ 



9,7oo 



77, 7 00 



72,300 



73^300 



/4',dt>o 
76,000 



3-9-23 cS/ee/cre/s ' ^>t./>cf/7c/&c/ /Ve/<2/. ^Ira^- //.^30 3^. J/J . /?e/- /¥. cyT yt,,^/^ 


//o//<3/r^j^e.-^ 
/i3./>e/~3^.y/-. 1 


,/■ 


^pe7r> 


4-0- 


4-6- 


.s-o' 


^-V 


6-0' 


&-6- 


7-a" 


7-6- 


s-o' 


9-0' 


7o-o' 


//-<?' 


/z-o' 


/3-0' 


/4-0- 


73-^ 


76-a' 


/7-a^ 




Co/fcre/^ 


c?/e^/ 


3" 


2/3 


764 


/27 


7aa 


79 


63 
97 


^/ 
79 


40 


32 


79 




















300 


S,4oo 


.75^ 


3/2 


239 


787 


/49 


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33 


34 


27 


















" 


9.£aa 


4 


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323 


23'6 


203 


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93 


77 


33 


36 


23 
















" 


/O,7oo 




344 


42/ 


333 


267 


2/8 


/79 


749 


724 


7,^4 


73 


37 


3tS 


22 














If 


//.7ao 


s 


677 


323 


4/6 


336 


274 


227 


739 


738 


733 


9S 


68 


4,9 


33 


2/ 












" 


/2.700 


6 


977 


7iia 


6a3 


490 


402 


334 


280 


237 


207 


747 


/a<f 


79 


37 


40 


27 










* 


/4,3<)0 


7 


7309 


702/ 


8/4 


66/ 


343 


434 


383 


324 


277 


2os 


733 


7/3 


36 


63 


43 


3/ 


/f 






" 


/^ooo 


<? 


733/ 


7/94 


933 


77S 


639 


333 


449 


38/ 


323 


24/ 


/8/ 


736 


/02 


73 


•S4 


•37 


24 






27S 




f 


/734 


7369 


7092 


888 


732 


6// 


3'/3 


438 


374 


^Tf 


209 


737 


7/9 


33 


64 


43 


29 






2SO 


1, 


/o 


7982 


/344 


/234 


7aa2 


826 


69a 


332 


494 


423 


3/4 


236 


779 


733- 


/a/ 


74 


32 


.5=^ 


/f 




233^ 





7/ . 


22 07 


7723 


/373 


///9- 


923 


777 


63/ 


333 


473 


332 


263 


20/ 


/32 


//4 


34 


6a 


4o 


23 




220 


>■ 


/z- 


2433 


/8?7 


73/3 


/233 


/^/7 


830 


7/7 


6/0 


322 


389 


293 


222 


763 


726 


93 


66 


44 


26 




2/0 


" 


3-9-30 ^/<^e-/cre-/e"^/(/}aais7ea7/fe/a/ Area" a.30a s^. //j.^er-//. of ly/i////. 


//a// tS/rcsses 
/Ss./>e/- s^./h. 


/ 


<5j(3on. 


4-0- 


4'-cr 


3-0' 


3-6" 


6-0' 


6-6" 


7-a- 


7-6' 


3-a' 


9-o' 


/a-o' 


//-o- 


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73-0' 


/4-0' 


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Coaerf/f 


c5>we/ 


3" 


226 


/73 


734 


/a6 


S3 


63 


34 


44 


33 


2/ 








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300 


7,400 


3i 


32f 


233 


79/f 


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34 


69 


37 


33 


24 


















* 


S,300 


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4^S 


3^6 


273 


2/9 


773 


746 


72/ 


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93 


33 


40 


26 
















* 


9.3ao 


^■s 


37^ 


446 


333 


284 


232 


79/ 


73f 


733 


7/2 


79 


36 


^9 


26 














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7O.400 


S 


72/ 


36o 


444 


.^9 


2f4 


243 


203 


/77 


744 


704 


7S 


34 


37 


23 












/' 


//,3ao 


6 


703d 


306 


6';iZ 


32/ 


428 


33^ 


2f9 


233 


2/6 


733 


777 


S7 


64 


4^ 


37 


20 








// 


/Z.900 


7 


/403 


/093 


873 


7// 


337 


49/ 


4/4 


332 


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224 


768 


723 


97 


72 


33 


38 


23 






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/4,400 


S 


/808 


74/3 


7/2f 


927 


767 


637 


33f 


439 


393 


296 


223 


/72 


/33 


702 


77 


•S7 


4/ 


27 




// 


/3,3oo 


f 


z/a-f 


/^/■^ 


/3/3 


7/>7Z 


3S8 


744 


629 


337 


462 


347 


Z64 


204 


737 


72/ 


93 


70 


3^/ 


33 


22 


230 


/6,aoo 


/a 


Z374 


7S33 


7^^4 


/Z/O 


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340 


7/0 


6/>6 


3Z2 


392 


Z99 


23/ 


/79 


/3fi 


706 


30 


38 


4/ 


26 


263 




// 


Z^4i. 


Z070 


7637 


733/ 


///9 


938 


794 


673 


383 


439 


336 


239 


20/ 


736 


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9/ 


67 


47 


37 


243 


« 


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Z9ZO 


ZZ83 


7828 


7490 


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876 


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644 


483 


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286 


222 


772 


733 


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73- 


33 


3S 


23S 


" 



120 



NOTES ON POWER PLANT DESIGN 



3-9-3S <5/eeATre/<?"^x/}a/?y£>£/ /Vie^/a/. y!r£-a =■ a.Ssa jf. /n. per- /Y. o/" kV/i//A \ 


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4-4- 


7-0- 


7-4' 


8-a' 


9-a' 


/a-a' 


//-a' 


72- a" 


/3-a' 


/4-a' 


/3-a' 


/4-a' 


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/8-a' 


Co/jcrd'A^ 


c5-/,?£-/ 


J" 


33S 


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74/) 


/// 


S8 


7/ 


37 


44 


37 


23 




















3aa 


4>.7aa 




343 


2ii4 


2^7 


/4^ 


734 


/a9 


89 


73 


4a 


4/ 


24 


















" 


7.4aa 


4 


^^-#' 


Ji/ 


28^ 


229 


787 


/JC3 


727 


/a4 


88 


42 


43 


29 
















ft 


8.4aa 


4^ 


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470 


372 


3ao 


244 


2a3 


749 


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7/9 


83- 


6/ 


43 


29 














i» 


9.4aa 


S 


^•r/ 


3S8 


4 £7 


377 


3 09 


237 


2/3 


78/ 


733 


/// 


8/ 


38 


4/ 


28 












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^ 


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8S/ 


47/1 


33/ 


434 


373 


3/8 


249 


23a 


749 


/24 


f4 


7a 


jr/ 


34 


24 








" 


//,7aa 


7 


/47.^ 


7/3/ 


9/f 


798 


4/^ 


3/7 


434 


37/ 


3/8 


237 


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737 


/a4 


79 


39 


43 


^f 






'• 


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S 


/■^o7 


/4?a 


7/73 


972 


3/^3 


474 


37/ 


487 


4/9 


3/3 


24a 


783 


/43 


/// 


83 


44 


47 


33 


2/ 


" 


/4.3/>a 


9 


237-^ 


//r.'iA 


/4S9 


72/3 


7aaS 


844 


7/8 


4/4 


329 


4aa 


3a8 


239 


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747 


7/3 


89 


48 


3a 


34 


" 


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^7iB 


2/64 


7733 


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7/74 


984 


837 


7/7 


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448 


34/ 


282 


22/ 


774 


737 


/a/ 


83 


42 


4^ 


29a 


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// 


3083 


24/4 


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/380 


73// 


//a/ 


933 


3a/ 


497 


323 


4a3 


3/4 


249 


797 


733 


722 


94 


7/ 


32 


27a 


■' 


/2' 


34:00 


2iio 


2/3S 


/744 


/44i 


/2/3 


/4>JZ 


884 


744 


379 


447 


33a 


273 


2/8 


772 


/3S 


/as 


8a 


3-9 


233 


" 


3-4 -40 <5/ee/c/'e-/e'~ ^x/>c/7a'ea^ /Ve/n^/ /^ret? = tP. 4oa Sf. //7 . />&/'/?. 0/" tv/d/M 


/63./>ersf./n- 


t,>'^ 


^yoa/7- 1 


4-0' 


4-li" 


3 -a' 


3-4" 


4-a 


4-4 


7-a- 


7-4- 


8-a- 


9-a 


/a-a' 


//-a- 


/2-a' 


/3-a' 


/4-a' 


/3-a' 


/4^' 


/7-a' 


/8-'a' 


Cancre/e 


^i^ee/ 


3" 


244 


/Sii 


743 


773 


92 


74 


4a 


49 


39 


23 




















3ao 


4./aa 


3i 


SS.^ 


273 


2/3 


77/ 


/39 


7/3 


93 


77 


43 


43 


28 


















" 


7.000 


-f 


■4S4 


374 


^fV 


238 


/94 


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732 


//a 


92 


43 


44 


3/ 


2a 














m 


7.Soa 


4^ 


li^/? 


4fi7 


387 


3/2 


234 


2// 


/74 


/48 


723 


?o 


44 


44 


32 


2/ 












m 


8.4ao 


S 


7fi7 


<i/2 


484 


394 


323 


248 


22^ 


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74/ 


7/7 


8d 


42 


4s 


3/ 


2a 










" 


9.4aa 


6 


//3S 


887 


708 


374 


474 


393 


332 


282 


24/ 


778 


/33 


/aa 


7S 


33 


4a 


27 








* 


/£>,8ao 


7 


/S4/ 


/2o3 


94/ 


783 


448 


342 


438 


390 


333 


23/ 


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744 


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83 


44 


47 


33 


22 




«■ 


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8 


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7a/4 


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7a3 


397 


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440 


33/ 


234 


794 


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7/9 


92 


7a 


32 


37 


23 


* 


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9 


247? 


7^42 


/334 


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7/>34 


834 


732 


444 


334 


42/ 


323 


233 


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737 


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94 


74 


34 


4/ 


* 


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30/f 


23^4 


/S7? 


/33/ 


7287 


/a83 


927 


79a 


433 


3/9 


402 


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23a 


/99 


/38 


723 


99 


74 


33 


♦ 


/S.400 


// 


3S/0 


27S3 


ZZ/O 


7Sas 


/3a/ 


7244 


7^73 


923 


799 


4a9 


473 


373 


297 237 


/9a 


732 


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9S 


73 


29S 


/4.aa0 


/2" 


3870 


303S 


243S 


/993 


7437 


7S9-S 


7/87 


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88/ 


473 


323 


4/2 


328 


242 


2/0^ 


'49 


/S4 


/a4 


82 


28a 


1 


3-4-^S "iSJ^e-e/cre'/e'" ^x./}a/7t/e-c/ /^fe/a/ y^rea = A ^sa sf. /h ./^e-/^/? of kv/o'/A 


4//7/Y<5fr^3ses. 
/63./>ffr3f. /h. 


¥ 


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4-a- 


4-<C 


^-a' 


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4 -a/ 


4-£' 


7-a' 


7'- 4' 


8-a' 


9-a' 


/a-a' 


//-a" 


/2-a' 


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/4-a' 


/£-a 


76- a' 


/7-a' 


/a-a' 


Ca/?cre';k 


S/'ee/. 


3' 


?.*/ 


792 


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9S 


77 


42 


^7 


4/ 


24 




















300 


S,4ao 


.T^ 


3ii. 


282 


222 


/77 


744 


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97 


8a 


^4 


43^ 


3a 


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" 


4. 400 


4 


^00 


38i 


3a 4 


244 


2'/>/ 


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//S 


94 


49 


48 


33 


22 














// 


7.2ao 


^# 


^49 


^as 


'^aa 


323 


244 


2/9 


783 


734 


730 


f4 


48 


49 


34 


22 












A 


S.aao 


S 


P/2 


632 


So3 


4o7 


33S 


278 


233 


797 


747 


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9a 


44 


48 


33 


22 










* 


6,700 


i 


//S2 


922 


734 


398 


493 


4/2 


.^47 


293 


232 


787 


/4a 


/a4 


8a 


S9 


43 


3o 


SO 






ft 


/a.aoa 


7 


/tia4 


7233 


7aa3 


ff/7 


474 


344_ 
733 


47f 


4a8 


33/ 


243 


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7/9 


9/ 


49 


32 


37 


24 




// 


//.2ao 


S 


20^ 


/i/i 


/2f4 


7^34 


873 


423 


332 


439 


347 


244 


2o4 


74/ 


/24 


98 


73 


37 


42 


29 


» 


/2,2oa 


? 


2S7? 


20/9 


74/9 


7324 


/i}f9 


923 


784 


472 


38a 


44a 


34a 


244 


2/a 


/44 


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/as 


8a 


42 


44 


'' 


/3.3oa 


/o 


3/39 


2439 


7974 


74/4 


7342 


//2f 


939 


824 


7/3 


^43 


^922 


332 


244 


2/a 


/48 


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/a4 


S3 


44 


* 


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// 


373S 


2930 


2333 


7923 


74a/ 


733a 


7/49 


988 


833 


434 


309 


4a3 


322 


239 


2a9 


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8S 


" 


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/2" 


^Jits 


34as 


2738 


224J 


7347 


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744 


399 


•973 


38o 


3a7 


249 


2a2 


/44 


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/as 


" 


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S-6-SO 'S/ee/ir/'£-/e''/^xpa/7a'ea^/Ve-/a/ Areir =a.SaO Sf. /n./ter /}<: ef ty/i//A 


4//}//^ S/r esses 
/As.pe/- sf. //>■ 


5\»^' 


<5p(?/7. 


4-0" 


4-4' 


3-0" 


3-4' 


4-cr 


4-4' 


7-'a' 


7-4- 


S-'o- 


9-0' 


/a^a' 


//-'a' 


/2-a' 


/3-a' 


74-a 


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/4-a 


/7-'a 


/8-a 


Co/7Cre/e 


c5/«/ 


4' 


S/3 


397 


3/S 


233 


207 


77/ 


742 


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7/ 


^0 


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23 














300 


4.7ao 


4^ 


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S/S 


4/7 


332 


2-72 


224 


789 


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77 


3/ 


J4 


24 












» 


7.4ao 


^ 


a34 


4SO 


S/7 


4/9 


344 


284 


24o 


2a3 


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724 


93 


49 


3i3 


34 


24 










m 


3./aa 


6 


/2/4 


949 


73/1 


4/4 


•3-a^ 


423 


338 


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24/ 


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744 


/// 


84 


43 


44 


33 


22 






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9.3ao 


7 


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//>33 


^43 


697 


^84 


494 


4?2 


S43 


273 


2a8 


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724 


94 


73 


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4a 


28 




" 


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8 


2/43 


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//)97 


9/a 


743 


448 


333 


478 


J42 


278 


2/7 


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8/ 


42 


-94 


33 


u 


//,Soo 


9 


2674 


2af4 


7479 


7374 


774a 


939 


8/3 


498 


404 


439 


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279 


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739 


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84 


47 


So 


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3244 


2344 


2044 


747/ 


7389 


7/49 


993 


839 


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344 


433 


344 


273 


220 


777 


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89 


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73^400 


// 


3^46 


303i 


2433 


79f3 


744a 


73f3 


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/a23 


S88 


479 


33/ 


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334 


277 


2/9 


777 


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7/3 


9/ 


« 


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433S 


3S4o 


2ff4o 


234S 


/932 


7443 


/4a3 


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Sa3 


429 


3^ao 


4a/ 


32S 


243 


2/4 


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/42 


7/S 


■' 


73. /OO 



NOTES ON POWER PLANT DESIGN 



121 



3-6 


■-SS 


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122 



NOTES ON POWER PLANT DESIGN 



Adjoining sheets should be lapped 8" on the end and one and one-half inches on the side. They 
should be wired together every three feet on the ends and every four feet on the sides. 

A reinforcing fabric known as the Triangle Mesh Concrete Reinforcement is manufactured 
by the American Steel and Wire Co. 

The tables which follow have been copied from an Engineer's Handbook published by the 
Company. 

This triangle mesh steel woven wire is made with both single and stranded longitudinal, or 
tension members. That with the single wire longitudinal is made with one wire varying in size 
from a No. 12 gauge up to and including a K" dia., and that with the standard longitudinal is 
composed of two or three wires varying from No. 12 gauge up to and including No. 4 wires stranded 
or twisted together. 

These longitudinals either stranded or solid are invariably spaced 4" centres, the sizes being 
varied in order to obtain the desird cross-sectional area of steel per foot of width. (See illustration.) 




Area ol S<eel Beqnirea per Fpot of Width lor a Mazimnm Resisting Moment at SUb o{ Given Thickneaa 

Cemaoalia SAFE BENDING MOMENT due to ipplled load and weijM ol fiooij 

M = ^ = A X Load per m. It. X (leaph of (pan)* = 



- BeadlDC MofflUt tor (lib fOppoiM m two tldM. 



The Maximmn Allowable Fiber Stress _ 

Id the concrete toxerns (he values above and to the tight ol this line. 

Ma^Kimtun StreM«at S<e«l 



the steel governs the vah.es o. ResisUn. Moments Eiven below a.d «. the' lei. ol Ute heavy '^^« ^Jj.'f •„^,»ta7/i'SJj'.^^^,f » 



• 16,000 Donnds. Cooere<e =• BSO pounds 



I l>2i 4 

I li2Ki5. oareinUy traded 



JiA 


•So 

II 
o2 


1 


" 


MOMENTS OF RESISTANCE IN FOOT POUNDS PER FO'OT OF WIDTH 












Iss 


CROSS SECTIONAL AREA IN SQUARE INCHES OF STEEL REINFORCEMENT PER FOOT OF WIDTH 




|i- 


.04 


.06 


.08 


.10 


.12 


.14 


.16 


.18 


.20 


■25 


.30 


.3a 


.40 


.45 


.50 


.55 


.60 


.65 


.70 


.75 


.80. 


.90 


1.00 


3 


% 

K 

X 

1 
1 
1 

1 
1 

m 
IK 


30 
36 
42- 

48 

54 
60 
66 
72 

78 
84 
90 
96 

102 
108 
114 
120 


86 
114 
137 
160 

192 


130 

165 
203 
237 

275 
313 
337 


168 
222 
268 
329 

377 
407 
455 
489 

■547 


210 
271 
332 
4D4 

458 
498 
572 
634 

678 
756 
764 


248 
327 
395 
478 

557 
589 
659 
742 

811 
913 
934 
1023 

1104 


289 
375 
458 
552 

636 
679 

774 
849 

941 
1017 
1103 
1156 

1257 
1346 
1437 


325 
423 
520 
625 

734 
769 
888 
991 

1071 
1172 
1216 
1S52 

1409 
1508 
1623 
1728 


341 


353 


377 
578 


611 

858 
1136 


900 
1194 

1519 


1246 

1585 
1764 


1644 
18a5 
2232 


1893 
2314 
2756 


2381 
2848 

3334 
3872 


2922 

3431 
3968 
42.'i5 


3525 
4072 
4371 
4963 


4169 
4464 
5080 

5725 
6077 


4259 
4566 
5207 

5860 
6200 
6914 


5309 

5987 
6340 
7055 
7836 


5498 

6201 
6576 
7338 
8114 




478 
592 
697 

812 

858 

973 

1095 

1199 
1326 
1383 
1483 

1636 
1670 
1807 
1936 


525 
653 
769 

890 
968 
1086 
1201 

1327 
1478 
1548 
1678 

1786 
1831 
1992 
2144 




3>^ 
4 


804 
954 

1100 
1187 
1337 
1513 

1664 
1831 
1877 
2062 

2232 
2309 
2447 
2660 




i}4 

5 
6 

7 
g 


1327 

1403 
1612 
1787 

1957 
2179 
2257 
2443 

2673 
2703 
2897 
3068 




1637 
1857 
2058 

2286 
2524 
2632 
2820 

3037 
3172 
3343 
a573 




2099 
2359 

2612 
2866 
2951 
3257 

3470 
3560 
3874 
4075 




2625 

2895 
3157 
3320 
3627 

3900 
4021 
4313 
4572 




3216 
3541 
3686 
3995 

4256 
4479 
4749 
5066 




3998 
4360 

4679 
4857 
5182 
5557 




4723 

5100 
5308 
5612 
6044 


5668 


8>i 
g 


5518 

6125 
6529 


6410 
6788 


10 


6550 


7571 


701l| 7395 


8393 













Maiimnm Strcaaeai Steel = 


= 16.000 pound 


a, Coiaorete = 700 ponnda 








Cone. 


Ii2i4 




is 


u 

oS 




MOMENTS OF RESISTANCE IN FOOT POUNJuS PER FOOT OF WIDTH 


lU 


CROSS SECTIONAL AREA IN SQUARE INCHES OF STEEL REINFORCEMENT PER FOOT OF WIDTH 


w 


.04 


.06 


.08 


.10 


.12 


.14 


.16 


.18 


.20 


.25 


.30 


a5 


.40 


.45 


.50 


.55 


.60 


.65 


.70 


.75 


.80 


.90 


1.00 


2V< 


X 

% 

X 
X 

IK 
IK 


30 
36 
42 

48 

54 
60 
66 
73 

78 
84 
90 
96 

102 
108 
U4 
120 


86 
114 
137 
160 

192 


130 
165 

2oa 

237 

275 
313 
337 


168 
222 
268 
329 

377 
407 
455 
489 

547 


210 
271 
332 
404 

458 
498 
572 
634 

678 
756 
764 


248 
327 
395 
478 

557 
589 
659 
742 

811 
913 
934 
1023 

1104 


289 
375 
458 
552 

636 
679 

774 
849 

941 
1017 
1103 
1156 

1257 
1346 
1437 


325 
423 
520 
625 

734 
769 
888 
991 

1071 
1172 
1216 
ia52 

1409 
1508 
1623 
1728 


366 
478 
592 
697 

812 

858 

973 

1095 

1199 
1326 
1383 
1483 

1636 
1670 
1807 
1936 


379 


406 
623 


658 
924 


969 
1286 


1342 
1707 


1770 
1976 


2038 
2492 


2.565 
3066 


3147 
3698 


3796 
4386 
4704 


4490 
4802 


4586 
4913 
5607 


5717 

6447 
6828 


5920 

6678 
7081 
7902 
8739 




3 


525 
653 
769 

890 
968 
1086 
1201 

1327 
1478 
1548 
1678 

1786 
1831 
1992 
2144 




3V< 


804 
954 

1100 
1187 
1337 
1513 

1664 
1831 
1877 
2062 

2232 
2309 
2447 
2660 




4 


1137 

1327 
1403 
1612 

1787 

1957 
2179 
2257 
2443 

2673 
2703 
2897 
3068 




i% 


1532 
1637 
1857 
2058 

2286 
2524 
2632 
2820 

3037 
3172 
3343 
$573 




5 


1849 
2098 
2359 

2612 
2866 
2951 
3257 

3470 
3560 
3874 
4075 




s^ 


2340 
2625 

2895 
3157 
3320 
3627 

3900 
4021 
4313 
4572 




6 


2889 

3216 
3541 
3686 
3995 

4256 
4479 
4749 
5066 




6^4 


3495 
3875 
3998 
4360 

4679 
4857 
5182 
5557 




7 
7^ 


416C 
435S 

4723 

51O0 
5308 
5612 
6044 




8 


5084 

5519 
5683 
6125 
6529 


5444 

5866 
6129 
6550 
7011 


6104 


9 


6280 
6500 
6973 
7395 


6903 
7310 


9^ 
10 


7395 
7968 


8154 
9038 













Moxunnm Streaaeat Sleel = 


= IS.OOO ponnda. Cotterete = 70U ponnd 








Cone. 


l>2i4 




Mx, 


II 

•So 

|s 

u 2 


'if 


MOMENTS OF RESISTANCE IN toOt POUNDS PER FOOT OF WIDTH 


S|| 


CROSS SECTIONAL AREA IN SQUARE INCHES OF STEEL REINFORCEMENT PER FOOT OF WIDTH 




.04 


.06 


.08. 


.10 


.15 


.14 


.16 


.18 


.20 


.25 


.30 


.35 


v40 


.45 


.50 


.55 


.60 


.65 


.70. 


.75 


.80 


.90 


1.00 


2K 


X 
X 
X 

X 

1 
1 

1 

1 
1 

IX 

■ IK. 
IK 
IK 


30 
36 
42 

■48 

54 
60 
66 
7? 

78 
84 
90 
96 

102 
108 

114 
120 


97 
128 
154 

J8C 

216 


146 
185 
228 
267 

309 
362 
379 


189 
250 
301 
370 

424 
456 
512 
550 

616 


237 
305 
373 
454 

515 
,560 
644 
714 

765 
851 
859 


276 
368 
444 
538 

627 
663 
741 
835 

' 913 
1027 
.1050 
1152 

1243 


325 

515 
621 

716 
764 
871 
956 

1059 
1144 
1240 

laoo 

1414 
1514 
1618 


353 


-367 


379 

579 


406 
623 

872 


658 

924 

1223 


968 
1286 

1636 
1821 


1342 

1707 
1899 
2316 


1770 
1976 
2404 
2871 


2038 
2492 
2968 

3489 


2560 
3066 

4442 


3147 

3898 
4274 
4579 
6210 


3796 
4386 
4704 
e34S 

6035 
6373 


4490 
4802 

6166 

6544 
7284 


4586 
4913 
5607 

6311 
6677 
7446 
8224 


5717 

6447 
6828 
7597 
8440 


5920 

6678 
7081 
7902 
8739 




3 


476 
585 
703 

g26 

865 

yyy 
1115 

1206 
1318 
1366 
1522 

1586 
1697 
1827 
1944 


.537 
666 

784 

914 

965 
1095 
1234 

1349 
1491 
1554 
1668 

1840 
1879 
2034 
2180 




3K 


734 
865 

1001 
1O90 

1352 

1493 
16^ 
1741 
1887 

2009 
2059 
2240 
2413 




4 


1074 

1238 
1336 

1702 

1872 
2059 
2110 
.2320 

2511 

K98 
2753 
2993 




4K 

5 


1493 
1578 
1814 
2010 

2200 
2452 
2537 
2749 

3006 
3041 
3259 
3451 




5K 


2089 
2315 

2573 

2840 
2958 
3173 

3416 
3569 
3761 
4O20 




6 


2654 

2938 
3225 
3318 
3664 

3906 
4004 
4358 

4584 




6J^ 


3257 
3551 
3T35 
4081 

4386 
4524 
4852 
5144 




7 


3984 
4143 
4494 

4789 
5700 




8 


4905 

6264 
5464 
5830 
6252 


6104 


8K 
9 


5738 
5972 
6313 
6810 


6903 
7310 


9K 


6890 
7345 


8154 


10 


7889 


9038 



124 



NOTES ON POWER PLANT DESIGN 



LONGITUDINALS SPACED 4-INCH CENTERS 

CROSS WIRES SPACED 4- INCH CENTERS 

Number and Gauge of Wires, Areas Per Foot Width and Weights Per 100 Square Feet 

Styles Marked * Usually Carried in Stock. 



Style 


No. of Wires 


Gauge of Wire 


Gauge of 


Sectional Area 


Sectional Area 


Cross Sectional 


Approximate 


Number 


Each Long 


Each Long 


Cross Wires 


Long. Sq. In. 


Cross Wires 


Area per Ft. 
Width 


Weight per 
100 Sq. Ft. 


*4 




6 


14 


.087 


.025 


.102 


43 


5 




8 


14 


.062 


.025 


.077 


34 


6 




10 


14 


.043 


.025 


.058 


27 


*7 




12 


14 


.026 


.025 


.041 


21 


*23 




K" 


12>^ 


.147 


.038 


.170 


72 


24 




4 


12J^ 


.119 


.038 


.142 


62 


25 




5 


12>^ 


.101 


.038 


.124 


55 


*26 




6 


nyi 


.087 


.038 


.110 


50 


*27 




8 


12K 


.062 


.038 


.085 


41 


28 




10 


12>^ 


.043 


.038 


.066 


34 


29 




12 


12K 


.026 


.038 


.049 


28 


31 


2 


4 


12K 


.238 


.038 


.261 


106 


32 


2 


5 


12K 


.202 


.038 


.225 


92 


33 


2 


6 


12K 


.174 


.038 


.196 


82 


34 


2 


8 


12>^ 


.124 


.038 


.146 


63 


35 


2 


10 


123^ 


.086 


.038 


.109 


50 


36 


2 


12 


12K 


.052 


.038 


.075 


37 


*38 


3 


4 


12>^ 


.358 


.038 . 


.380 


151 


39 


3 


5 


12K 


.303 


.038 


.325 


130 


40 


3 


6 


12K 


.260 


.038 


.283 


114 


41 


3 


8 


12K 


.185 


.038 


.208 


87 


*42 


3 


10 


12K 


.129 


.038 


.151 


66 


43 


3 


12 


liyi ' 


.078 


.038 


.101 


47 



LENGTH OF ROLLS: 150-ft., 300-ft. and 600-ft. 

WIDTHS: 18-in., 22-in., 26-in., 30-in., 34-in., 38-in., 42-in., 46-in., 50in., 54-in. and 58-in. 



LONGITUDINAL SPACED 4-INCH CENTERS 

CROSS WIRES SPACED 2-INCH CENTERS 

Number and Gauge of Wires, Areas Per Foot Width and Weights Per 100 Square Feet 

Styles Marked * Usually Carried in Stock 



Style 


No. of Wires 


Gauge of Wire 


Gauge of Cross 


Sectional Area 


Sectional Area 


Cross Sectional 


Approximate 


^lunber 


Each Long 


Each Long 


Wires 


Long. Sq. In. 


Cross Wires 
Sq. In. 


Area per Ft. 
Width 


Weight per 
100 Sq. Ft. 


4-A 




6 


14 


.087 


.050 


.102 


53 


5-A 




8 


14 


.062 


.050 


.077 


44 


6-A 




10 


14 


.043 


.050 


.058 


37 


* 7-A 




12 


14 


.026 


.050 


.041 


31 


23-A 




K" 


12K 


.147 


.076 


.170 


86 


24-A 




4 


12K 


.119 


.076 


.142 


76 


25-A 




5 


\2y^ 


.101 


.076 


.124 


70 


26-A 




6 


viyi 


.087 


.076 


.110 


64 


27-A 




8 


i2y2 


.062 


.076 


.085 


55 


*28-A 




10 


12K 


.043 


.076 


.066 


48 


29-A 




12 


12K 


.026 


.076 


.049 


42 


31-A 


2 


4 


12K 


.238 


.076 


.261 


120 


32-A 


2 


5 


i2y2 


.202 


.076 


.225 


107 


33-A 


2 


6 


12K 


.174 


.076 


.196 


97 


34-A 


2 


8 


12K 


,124 


.076 


.146 


78 


35-A 


2 


10 


12K 


.086 


.076 


.109 


64 


36-A 


2 


12 


12>^ 


.052 


.076 


.075 


52 


38-A 


3 


4 


12^ 


.358 


.076 


.380 


165 


39A 


3 


5 


viy 


.303 


.076 


.325 


145 


40-A 


3 


6 


12K 


.260 


.076 


.283 


129 


41-A 


3 


8 


i2y2 


.185 


.076 


.208 


101 


42-A 


3 


10 


12K 


.129 


.076 


.151 


81 


43-A 


3 


12 


12K 


.078 


.076 


.101 


62 



LENGTH OF ROLLS: 150-ft., 300-ft. and 600-ft. 

WIDTHS: 18-in., 22-)n., 26- in., 30-in., 34-in.. 38-in., 42-in., 46-in., 50-in., 54-in. and 58-in. 



NOTES ON POWER PLANT DESIGN 



125 



This table taken from the Engineer's Handbook gotten out by the American Steel and Wire 
Co. contains information which may be of use. 



Mixtures 




Required for 1 cub 


ic yard ram 


med concrete 




Stone 




Stone 


Gravel 






1 in. 


and under. 


2* in 


and under. 








dust screened out 


dust screened out 


J in. and under 








" i2' 




. 


m- m 








-o ^ 




■S -o 


-0 T3 






, '^ 


>. >> 


,. m 


>> >> 


•A ^ ^ 


a 




c3 


3 .3 


^^ 


3' .3' 


C-5 3 -TfS 


S a 


a 
o 


g 


a o 


g 


- 0) 

c 


r T V 


a c3 


^ 


S 


C3 -S 


0) 


a a 


V a t-t 


O ra 


M 


O 


m m 


O 


w m 


w 


1 1.0 


2.0 


2.57 


0.39 0.78 


2.63 


0.40 0.80 


2.30 0.35 0.74 


1 1.0 


2.5 


2.29 


0.35 0.70 


2.34 


0.36 0.89 


2.10 0.32 0.80 


1 1.0 


3.0 


2.06 


0.31 0.94 


2.10 


0..32 0.96 


1.89 0.29 0.86 


1 1.0 


3.5 


1.84 


0.28 0.98 


1.88 


0.29 1.00 


1.71 0.26 0.91 


1 1.5 


2.5 


2.05 


0.47 0.78 


2.09 


0.48 0.80 


1.83 0.42 0.73 


1 1.5 


3.0 


1.85 


0.42 0.84 


1.90 


0.43 0.87 


1.71 0.39 0.78 


1 1.5 


3.5 


1.72 


0.39 0.91 


1.74 


0.40 0.93 


1.57 0.36 0.83 


1 1.5 


4.0 


1.57 


0.36 0.96 


1.61 


0.37 0.98 


1.46 0.33 0.88 


1 1.5 


4.5 


1.43 


0.33 0.98 


1.46 


0.33 1.00 


1.34 0.31 0.91 


1 2.0 


3.0 


1.70 


0.52 0.77 


1.73 


0.53 0.79 


1.54 0.47 0.73 


1 2.0 


3.5 


1.57 


0.48 0.83 


1.61 


0.49 0.85 


1.44 0.44 0.77 


1 2.0 


4.0 


1.46 


0.44 0.89 


1.48 


0.45 0.90 


1.34 0.41 0.81 


1 2.0 


4.5 


1.36 


0.42 0.93 


1.38 


0.42 0.95 


1.26 0.38 0.86 


1 2.0 


5.0 


1.27 


0.39 0.97 


1.29 


0.39 0.98 


1.17 0.36 0.89 


1 2.5 


3.5 


1.45 


0.55 0.77 


1.48 


0.56 0.79 


1.32 0.50 0.70 


1 2.5 


4.0 


1.35 


0.52 0.82 


1.38 


0.53 0.84 


1.24 0.47 0.75 


1 2.5 


4.5 


1.27 


0.48 0.87 


1.29 


0.49 0.88 


1.16 0.44 0.80 


1 2.5 


5.0 


1.19 


0.46 0.91 


1.21 


0.46 0.92 


1.10 0.42 0.83 


1 2.5 


5.5 


1.13 


0.43 0.94 


1.15 


0.44 0.96 


1.03 0.39 0.86 


1 2.5 


6.0 


1.07 


0.41 0.97 


1.07 


0.41 0.98 


0.98 0.37 0.89 


I 3.0 


4.0 


1.26 


0.58 0.77 


1.28 


0.58 0.78 


1.15 0.52 0.72 


1 3.0 


4.5 


1.18 


.0.54 0.81 


1.20 


0.55 0.82 


1.09 0.50 0.75 


1 3.0 


5.0 


1.11 


0.51 0.85 


1.14 


0.52 0.87 


1.03 0.47 0.78 


1 3.0 


5.5 


1.06 


0.48 0.89 


1.07 


0.49 0.90 


0.97 0.44 0.81 


1 3.0 


6.0 


1.01 


0.46 0.92 


1.02 


0.47 0.93 


0.92 0.42 0.84 


1 3.0 


6.5 


0.96 


0.44 0.95 


0.98 


0.44 0.96 


0.88 0.40 0.87 


1 3.0 


7.0 


0.91 


0.42 0.97 


0.92 


0.42 0.98 


0.84 0.38 0.89 


1 3.5 


5.0 


1.05 


0.56 0.80 


1.07 


0.57 0.82 


0.96 0.50 0.76 


1 3.5 


5.5 


1.00 


0.53 0.84 


1.02 


0.54 0.85 


0.92 0.48 0.78 


1 3.5 


6.0 


0.95 


0.50 0.87 


0.97 


0.51 0.89 


0.88 0.46 0.80 


1 3.5 


6.5 


0.92 


0.49 0.91 


0.93 


0.49 0.92 


0.83 0.44 0.82- 


.1 3.5 


7.0 


0.87 


0.47 0.93 


0.89 


0.47 0.95 


0.80 0.43 0.85 


1 3.5 


7.5 


0.84 


0.45 0.96 


0.86 


0.45 0.-98 


0.76 0.41 0.87 


1 3.5 


8.0 


0.80 


0.42 0.97 


0.82 


0.43 1.01 


0.73 0.39 0.89 


1 4,0 


6.0 


0.90 


0.55 0.82 


0.92 


0.56 0.84 


0.83 0.51 0.77 


1 4.0 


6.5 


0.87 


0.53 0.85 


0.88 


0.53 0.87 


0.80 0.49 0.79 


1 4.0 


7.0 


0.83 


0.51 0.89 


0.84 


0.51 0.90 


0.77 0.47 0.81 


1 4.0 


7.5 


0.80 


0.49 0.91 


0.81 


0.50 0-.93 


0.73 0.44 0.83 


1 4.0 


8.0 


0.77 


0.47 0.93 


0.78 


0.48 0.95 


0.71 0.43 0.86 


1 4.0 


8.5 


0.74 


0.45 0.95 


0.76 


0.46 0.98 


0.68 0.42 0.88 


1 4.0 


9.0 


0.71 


0.43 0.97 


0.73 


0.44 1.01 


0.65 0.40 0.89 



I bbl. cement & 2 bbl. sand will cover 99 sq. ft. of floor i in. thick. 
I ' " J « << << .■< 68 .. « .< a J << << 



126 



NOTES ON POWER PLANT DESIGN 



COSTS 

To give an idea as to the relative costs of the different items entering into the total cost of a 
Power House two tables have been given. It is seen from these tabulations that the total cost 
per K. W. exclusive of the land is around $105 for a station of moderate size and goes as low as $60 
for large stations. 

In one station the cost of piping may be greater than that in another of the same size. This 
may be offset, however, by the lower cost of some other item so that the total cost of the two does 
not differ much. 



and discharge and buildings 



$3.50 

15.00 

3.50 



POWER HOUSE COST PER RATED K. W. INSTALLED Max 
Foundations ...... 

Sidings, roadways, circulating water intake 
Chimneys and flues .... 

Building Total $22.50 

Boilers, installed 14.00 

Superheater . . . . . . . . . . . . 1.50 

Stokers 10.00 

Economizers . . . . . . . . . . . . 5.00 

Coal Conveyor and bunkers . . . . . . . . . 6.00 

Ash conveyor . . . , . . . . . . . 1 . 50 

Piping and pipe covering . . . . . . . . . 12 . 00 

Feed pumps . . . . . . . . . . . . 1 . 00 

Feed water heater • . . . . . . , . . . . 2 . 00 

Turbine and generator . . . . . . . . . . 15 . 00 

Condenser, jet type . . . . . . . . . . 3.00 

Exciter 1,50 

Switchboard 4.00 

Cables and conduits in power house . . . . . . . . 6 . 00 

Incidentals ............ 2.00 

Machinery Total 
Grand Total 



Min. 

$1.50 

8.00 

2.50 



$12.50 
8.00 
1.00 



00 
00 
00 
00 



6.00 
1.00 
1.00 
12.00 
2.50 
.75 
2.50 
3.00 
2.00 



,50 
106.50 



60 



,75 
25 



Koester in Steam Electric Power Plants gives the following tabulations of costs for plants of 
3000 to 5000 K.W. capacity. 



COST OF TURBINE PLANTS 
3000 to 5000 K. W. — per K. W. 



Min. Max. 



Excavations and Foundations 

Building 

Tunnels . 

Flues and Stacks 

Boilers and Stokers . 

Superheaters 

Economizers . 

Coal and Ash System 

Blowers and Ducts . 

Pumps and Tanks . 

Piping complete 

Turbo-Generators . 

Condensers — surface 

Exciters . 

Cranes . 

Switchboard . 

Labor and Incidentals 



$2.00 

10.00 

1.75 

2.50 

8.50 

2.00 

2.00 

1.50 

1.00 

1.00 

2.25 

22.00 

5.00 

.75 

.25 

2.00 

1.00 



$2.50 

15.00 
4.00 
3.50 

12.00 
2.50 
2.25 
3.00 
1.50 
1.25 
4.50 

25.00 
8.00 
1.00 
.50 
3.50 
2.00 



$65.00 $92.00 



NOTES ON POWER PLANT DESIGN 127 

COST OF EXCAVATION FOR FOUNDATIONS 

Cost per cubic yard 















Poor Sand 


Pile onf 














or 


wet clay 








Good" 


Good" 


Good* 


dry crib 


or 






Ledge 


Gravel 


Sand 


Clay 


Work 


Sand 


1st 


5 ft. 


2.00 


0.40 


0.30 


0.25 


0.50 


0.60 


2nd. 


5 ft. 


2.75 


0.60 


0.50 


0.35 


0.70 


0.75 


3rd. 


5 ft. 


3.50 


0.80 


0.70 


0.80 


1.00 


1.50 



° Some bracing of banks required. 

* No bracing of banks required (large quantities excavated), 

t Average for 15 feet depth without sheet piling $0.90. 

Average for 15 feet depth with sheet piling $1.00. 
Rock excavation $2.00 to $3.00 per cu. yd. 
Cement costs from $1.30 to $1.50 per bbl. 
Sand costs $1.00 per cu. yd. delivered. 
Stone costs $1.00 per cu. yd. at crusher. 
Concrete footings concrete alone costs $7.20 per cu. yd. 
Forms cost about 12 cents a sq. ft. 

A rough estimate of the cost of a footing including excavation, concrete and forms may be 
made by figuring the concrete at $9.00 per cubic yard. 

PILES 

Oak piles 20-30 ft. long 12" butt 6" top, 17 cents per ft. of length. 
Oak piles 40-60 ft. long, 21 to 25 cents per ft. of length. 
Spruce piles 20-30 ft. long 10" butt, 15 cents per ft. of length. 
Cost of driving and cutting off, 9 cents per ft. of length. 
Concrete piles in place from $1.25 to $1.50 per ft. of length. 

BRICKS 

Bricks per 1000, $7.50 to $10.00. 

Cost of laying 1000 bricks in a wall 10" to 12" thick including mason, helper and staging is 
$8 to $8.50. 1000 bricks laid make 2 cu. yds. masonry and cost $16 to $18. 

CONCRETE WALLS AND FLOORS 

Concrete forms for floors, 12 cts. per sq. ft. 

Concrete forms for walls (2 sides) 24 cents sq. ft. wall area. 

Concrete wall 6" thick including forms, costs, 40 cents per sq. ft. 

Concrete, $7.20 cu. yard. 

If there is no abnormal amount of reinforcement the cost of a floor may be figured by adding 
the cost of the form 12 cents per sq. ft. to the cost of the concrete per sq. ft. which is $.0222 x thick- 
ness of floor in inches. 

Where there is an abnormal amoimt of reinforcement the cost of the steel should be considered. 



STEEL FRAMEWORK 

The cost of structural steel work varies with the price of steel and fluctuates between $45 and 
$75 per ton erected. 

" In general $60 a ton is a safe figure to use. 



128 



NOTES ON POWER PLANT DESIGN 



FLUES, DAMPERS, ETC. 

Flues should be figured by the cost per pound. A flue {}4" thick) without difficult bends may 
be estimated at 10 cents per pound erected. A flue may cost as much as 15 cents a pound where 
there is difficulty in erecting it on account of lack of space. 



BOILERS 
A high pressure water tube boiler 

400 to 800 H. P. per unit, $16.50 H. P. erected. 
Superheater for same, f 1.50 to $1.00 per H. P. 



ECONOMIZERS 
Economizers 110 to $12 per tube erected or about * 



.50 per Boiler Horse Power. 



Stokers cost from 



STOKERS 
to $10 per rated H. P. of boiler. 



CHIMNEYS 

The cost of Radial Brick Chimneys is approximately as given below. 
These costs being for the structure above the foundations. 



Height 








Top diams. 


in ft. 




Ft. 


4 


6 


8 


10 


12 


14 


75 


1400 


2000 


2700 


3700 






125 




3500 


4300 


4700 


5100 




150 






6200 


7200 


7800 


8300 


175 






7000 


8000 


9000 


9800 


200 








10500 


11000 


12500 


250 








16500 


18300 


22000 



16 



24300 



The comparative total costs of a chimney 150 ft. tall 8 ft. diam. as given by Christie in "Chim- 
ney Design and Theory" are: 



Red brick .... 
Radial brick 

Steel, self supporting full lined 
Steel, self supporting half lined 
Steel, self supporting unlined 
Steel guyed .... 



$8500 



$5820 



COAL CONVEYOR 



For a station of 15000 K. W. capacity about 
1000 K. W. about $4.00 per K. W. 



.15 per K.W.; for 5000 K.W. about $2.50; for 



COAL BUNKERS 

For parabolic form estimate steel if of suspended type, rods or straps as $100 per ton erected, 
if of steel plate $75 per ton erected. Add to this the cost of the concrete lining. 
If of girder type figure steel as $65 per ton and add cost of concrete. 



NOTES ON POWER PLANT DESIGN 



129 



TURBINES AND GENERATORS 

Price depends upon market conditions but generally around $13 K. W. 

Some quotations obtained in February, 1915, at a time when steel was low in price were as 
follows : 



Turbine and Genebator 



2000 K. W. . 
G. E. Co. 2000 K. W. bleeder type 

1000 K. W. . 

2000 . 
Westinghouse 2000 bleeder . 

1000 . 
A Le Blanc condenser for the 

2000 K. W. cost .... 
1000 K. W. cost .... 

A cooling tower for 3000 K. W. 26" vacuum $7,800 above foundation. 



$23,000 
$24,000 
$13,500 

$18,500 
$19,500 
$13,000 

$4250 



COMPARISON OF COSTS OF DIFFERENT TYPES OF ENGINES* 









Steam Consumption 


Cost per 


H. P. 




Cylinders 


Speed 


Exhaust 


Lbs. per I. 


H. P. hr. 






Total 








non cond'g 


cond'g 


Engine 
erected 


Bldgs. 

Boilers 

Chimney 


cost 


Simple 


High speed 


Non-cond'g 


33 


— . 


$17.50 


$15.20 


$32.70 




High speed 


Cond'g 


— 


22 


21.00 


12.00 


33.00 




Low speed 


Non-cond'g 


29 


— 


25.00 


14.20 


39.20 




Low speed 


Cond'g 


— 


20 


27.00 


11.50 


38.50 


Compound 


High speed 


Non-cond'g 


26 


— 


21.00 


13.10 


34.60 




High speed 


Cond'g 


— 


20 


24.50 


11.40 


35.90 




Low speed 


Cond'g 


— 


18 


30.00 


11.00 


41.00 


Triple Exp. 


High speed 


Non-cond'g 


24 


— 


26.00 


12.50 


38.50 




High speed 


Cond'g 


— 


17 


29.00 


10.50 


39.50 




Low speed 


Cond'g 


— 


16 


37.50 


10.30 


47.80 



""From Mr. Chas. E. Emery. 



The following pages giving the Cost of Steam and Power Plant Equipment were taken from 
an Article by Professor A. A. Potter, M. I. T. 1903, in Power, December 30, 1913. 



130 



NOTES ON POWER PLANT DESIGN 



TABLE OF COSTS OF STEAM AND GAS POWER-PLANT EQUIPMENT 



Name of Apparatus 
Air compressora 



Boilers, steam 



Condensers 



Economizers 



Type 
Single cylinder, belt-driven 
Duplex, belt-driveri 
Compound, belt-driven 
Single cylinder, f-team-driven 
Duplex, steam-driven 
Compound, steam-driven 
Vertical, fire-tube 

Submerged tubes, 100 lb. per sq. in. or less 
Full length tubes; 100 lb. per sq. in. or less 
Horizontal, fire-tube cylindrical, multi- 
tubulai, 100 lb. per sq. in. or less 



Portable locomotive 

Vertical, water-tube, pressures over 125 lb. 

per sq. in. 
Horizontal, water-tube, pressures over 125 

lb. per sq, in. 
Barometric (28-in. vacuum) 
Jet condensers 



Fans and blowers 
Feed-water heaters 



Generators, electric 



Motors, electric 



Capacity 
Up to 4000 cu. ft. per rnin. 
Up to 850 cu. ft. per min. 
Up to 550 cu. ft. per min. 
Up to 350 ou. ft. per min. 
Up to 600 cu. ft. per min. 
Up to 500 cu. ft. per min. 
Under 20 hp. 
20 to 50 hp. 
Up to 50 hp. 

Up to 200 hp. 
Up to 100 hp. 
100 hp. to 225 hp. 
Up to 100 hp. 



Surface condensers 



Number of tubes 32 to 10,000, heating sur- 
face per tube = 12 to 13 sq. ft. 



Engines, internal combustion 



Engines, steam 



Gas engines 

Gasoline engines, hit-and-miss governor 

Gasoline engines, throttling governor 

Oil engines 

Producer gas engines, American mfg. 

Simple, 

Throttling governor, slide valve, vertical Up to 70 hp. 

Throttling governor, slide valve, horizontal 



100 to 500 hp. 

100 to 600 hp. 
Up to 30,000 lb. of steam per hr. 
Up to 30,000 lb. of steam per hour; 

28-in vacuum. 
26-in. vacuum 
Up to 35,000 lb. of steam per hr.; 28-in. 

vacuum 
Up to 30,000 lb. of steam per hr. ; 26-in. 

vacuum 
Capacity in lb . of water per tube = 60 

to 70 
Economizer alone 
Economizer erected 
Up to 300 hp. 
Up to 100 hp. 
Up to 75 hp. 
Up to 400 hp. 
Up to 300 hp. 



Equation of Cost in Dollars 
52 -t- 1.95 X cu. ft. 
316 4- 1.675 X cu. ft. 
3.1 X cu. ft. 
231 -I- 2.32 X cu. ft. 
460 + 2.55 X cu. ft. 
71.25 -f 4.025 X cu. ft. 
49.2 4- 6.66 X hp. 
116.4 -I- 3..35 X hp. 
51.5 + 3.62 X hp. 

64 -f- 4.14 X hp. 
5.8 X hp. - 20 
211 -f- 3.35 X hp. 
121 + 5.68 X hp. 

912 -I- 6.28 X hp. 

149 + 8.24 X hp. 
1055 -1-0.112 X (lb. steam cond.) 

1176 -I- 0.1138 X (lb. steam cond.) 
116 -f- 0.0591 X (lb. steam cond.) 

1630 -I- 0.2038 X (lb. steam cond.) 

413 + 0.1015 X (lb. steam cond.) 



Upper limit in cost 

Lower limit in cost 
Simple, 

Flywheel governor, piston or balanced 
slide valve, horizontal 
Automatic cut-ofi, single valve, vertical 

Flywheel governor, Corliss non-releasing 

valve, horizontal 
Corliss governor and valves, horizontal 

Flywheel governor, multiple fiat valves 
Cross compound, 

Ball governor, single-valve, horizontal 
Ball governor, single-valve, vertical 
Flywheel governor, multiported valves, 

horizontal 
Shaft governor, Corliss non-releasing 
valves, horizontal 
Tandem compound. 

Flywheel governor and slide valves, hori- 
zontal 
Flywheel governor and slide valves, ver- 
tical 
Flywheel governor, Corliss non-releasing 

valves, horizontal 
Flywheel governor, multiple slide valves 
Sizes 70to 140 in. 
Open 

Closed 

Direct current (voltage 110-2.50), belted 

Direct-connected 

.Alternating-current, belted 
Direct-connected 

Direct-current, belted ; smzll sizes 



Variable speed 

Alternating current: 

Single-phase (110-220 volts) 
Belted ; polyphase induction 

Variable speed 



Up to 70 hp. 
Up to 200 hp. 



$8 to $10 per tube 
$12 to $15 per tube 
33.6 X hp. - 115 
141 + 24.8 X hp. 
309 -t- 36.1 X hp. 
63.8 X hp. - 316 
400 -f 33.5 X kp. 

63.5 -I- 17.5 X hp. 

107 + 13.3 X hp. 
80 -f- 5.81 X hp. 



Up to 500 hp. 
Up to 30 hp. 
30 to 150 hp. 

Up to 600 hp. 
Up to 400 hp. 
300 to 900 hp. 
Up to 400 hp. 

Up to 330 hp. 
Up to 200 hp. 

Up to 600 hp. 

Up to 600 hp. 

Up to 400 hp. 

Up to 140 hp. 

Up to 300 hp. 
Up to 500 hp. 

Up to 1500 boiler hp. 
1500 to 3000 boiler hp. 
Up to 3000 boiler hp. 
Up to 7 kw. (1400 to 2300 r.p.m.) 
10 kw. to 300 kw. (600 to 1400 r.p.m.) 
Up to 300 kw. (100 to 350 r.p.m.) 
300 to 1000 kw. (moderate speed) 
Up to 300 kv.a. (600 to 1800 r.p.m.) 
Up to 300 kv.a. (200 to 300 r.p.m.) 
250 to 2500 kv.a. (100 to 250 r.p.m.) 
Up to 1.5 hp. (1400 to 2500 r.p.m.) 
1.5 to 30 hp. (1000 to 1800 r.p.m.) 
30 to 100 hp.— Upper limit (500 to 800 

r.p.m.) 
Lower limit— (800 to 1000 r.p.m.) 
Up to 10 hp. — Upper limit 

Lower hmit 

Up to 25 hp. (1200 to 1800 r.p.m.) 
Up to 130 hp. (1200 to 1800 r.p.m.) 
Up to 25 hp. 
35 to 60 hp. 



386 -I- 6.69 X hp. 
164 + 9.53 X hp. 
372.5 -I- 9.55 X hp. 

1100 -I- 8.94 X hp. 
1040 -I- 8.45 X hp. 
730 -i- 9.1 X hp. 
685 -I- 7.69 X hp. 

735 -I- 8.0 X hp. 
750 -I- 10.4 X hp. 

1100 -1- 9.62 X hp. 

2015 + 9.74 X hp. 

559 -I- 8.83 X hp. 

610 + 12.7 X hp. 

1295 -I- 10.79 X hp. ' 
1010 -I- 7.65 X hp. 
6.25 X (size in inches) 

114.5 + 0.3787 X hp. 
326 -I- 0.237 X hp. 
40 -I- 0.72 X hp. 
21.1 + 28.5 X kw. 

10 X (kw.) — 9 
313.3 + 10.93 X kw. 
12.08 X (kw.) - 383 
81 -I- 9.723 X kv.a. 
375 -I- 7.477 X kv.a. 
2413 -I- 4.69 X kv.a. 
18..53 -I- 42.37 X hp. 
53.3 -t- 12.4 X hp. 

191.7 -I- 10.94 X hp. 
213 -I- 8.264 X hp. 

64.1 4- ,36.786 X hp. 

69.2 -I- 10.56 X hp. 

25 -t- 11.75 X hp. 
116 -I- 4.72 X hp. 
60.7 -f- 7.15 X hp. 

157.6 + 3.573 X hp. 



NOTES ON POWER PLANT DESIGN 



131 



TABLE OF COSTS OF STEAM AND GAS POWER-PLANT EQUIPMENT - 



Name of Apparatus 
Producers, gas 

Producer plants, gas 
Pumps 



Purification plants 

Stokers 



Superheaters 



Transformers 



Turbines, steam 



Type 

Suction 
Pressure 
Suction 
Boiler feed 

Single-cylinder, piston pattern 

Duplex, piston pattern 
Single-cylinder, out«ide-packed, plunger 

pattern 
Duplex, outside-packed plunger pattern 
Centrifugal 

Horizontal, low-pressure, single-stage 
Horizontal, high-pressure, single-stage 

Horizontal, high-pressure, multi-stage 
Vertical, low-pressure, single-stage 
Vertical, high-pressure, single-stage 
Vertical, high-pressure, multi-stage 

Geared power 
Single cylinder 
Single-acting, triplex 
Double-acting, triplex 

Rotary force pumps 

Wet vacuum pumps 

Water 
Chain-grate 

Front-feed 
Under-feed 
200 to 750 boiler hp. 



Air-cooled 
Oil-cooled 



Water-cooled 

Reaction type : 

Turbine and generator 

Impulse type : 
Turbine alone 

Turbine and generator 



Capacity 

Up to 300 hp. 
Up to 300 hp. 
Up to 200 hp. 

Up to 6000 gal. per hr. 
6000 to 27,000 gal. per hr. 
Up to 29,000 gal. per hr. 

Up to 24,000 gal. per hr. 
Up to 49;000 gal. per hr. 

Up to 14,000 gal. per rain. 
Up to 5000 gal. per min. 
5000 to 20,000 gal. per min. 
Up to 2200 gal. per min. 
Up to 20,000 gal. per min. 
Up to 20.000 gal. per min. 
Up to 1100 gal. per min. 

Up to 20,000 gal. per hr. 
Up to 83,000 gal. per hr. 
Up to 89,000 gal. per hr. 
1200 to 20,000 gal. per hr. 
Up to 13,000 gal. per hr. 
13,000 to 50,000 gal. per hr. 
1000 to 20,000 gal. per hr. 
100 to 300 boiler hp. 
300 to 500 boiler hp. 
100 to 660 boiler hp. 
Up to 600 boiler hp. 

100 deg. of superheat 

200 deg. of superheat 

300 deg. of superheat 
Sizes up to 3000 ky. a 
Sizes up to 30 kv.a. 

25 cycles 

60 cycles 
Sizes 30 to 100 kv.a. 

25 cycles 

60 cycles 
Sizes up to 1000 kv.a. 
1000 to 3000 kv.a. 

500 to 5000 kw. 
5000 to 10,000 kw. 

Up to 50 hp. 
50 to 400 hp. 
Up to 40 kw. 
25 to 350 kw. 
1000 to 10,000 kw. 



- Continued 

Equation of Cost in Dollars 

252 + 14.2 X hp. 
860 + 15.15 X hp. 
570 + 46.5 X hp. 

17.8 + 0.2586 X (gal. per hr.) 
106.8 + 0.011045 X (gal. per hr.) 
585 + 0.0115 X (gal. per hr.) 

0.034 X (gal. per hr.) 
" 0.042125 X (gal. per hr.) 

52 -I- 0.05525 X (gal. per min.) 
61 -I- 0.0868 X (gal. per min.) 
210 + 0.05R7 X (gal. per min.) 
117-1- 0.233 X (gal. pei min.) 
60 + 0.05575 X (gal. per min.) 
50 -I- 0.0865 X (gal. per min.) 
12,5.7 + 0.27 X (gal. per min.) 

90 -f- 0.0316 X (gal. per hr.) 
56 + 0.03867 X (gal. per hr.) 
195 -I- 0.0148 X (gal. per hr.) 
8 4-0.0117 X (gal. perhr.) 
18 + 0.01435 X (gal. per hr.) 
14 + 0.00863 X (gal. per hr.) 
1000 -t-0.2 X (gal. perhr.) 
86 -t-4.28 X(hp.)j 
434 4-3.1 X(hp.) f 
312 4-3.015 X (hp.) 
379 4-2.785 X (hp.) 

165 4- 2.578 X (hp.) 
52 4-3 466 X (hp.) 
40 4- 4.28 X (hp.) 
439 4- 1.467 X kv.a. 

52.9 4- 8.1 X kv.a. 
26.2 4- 6.25 X kv.a. 

157 4- 4.68 X kv.a. 
119.5 4- 3.57 X kv.a. 
181 4- 1725 X kv.a. 
805 4- 1099 X kv.a. 

3335 4- 13.33 X kw. 
17,500 4- 10.5 X kw. 

171.5 4- 10.7 X hp. 
10.74 X hp. — 54 
304.2 4- 36.78 X kw. 
30.4 X kw. - 100 
8106 4- 11.34 Xkw. 



132 



NOTES ON POWER PLANT DESIGN 



The "Load Factor" = 



LOAD FACTOR 

Yearly output in K. W. hrs. 
8760 X rated capacity in K.W. 



or 



The Station Load Factor = 



Yearly output in H. P. hrs. 
8760 X rated capacity in H.P. 

8760 = 24 X 365. 

Yearly output K. W. hrs. 



Rated capacity in K. W. x hrs. plant ran 



It is evident that the higher the load factor the cheaper the cost per K. W. hr. or per H. P. 
hr. becomes, inasmuch as the fixed charges are the same whether the plant is running at half load, 
full load, full time, half time or idle. 

If a plant had to be run continuously it would be advisable to have at least one spare unit 
and due to the cost of this spare unit the fixed charge would be greater than for a plant which was 
idle at night and hence gave opportunity to make repairs, so that a spare unit was not necessary. 



COST OF OPERATION 

The cost of operation of a power plant may be divided into: 
A. Fixed charges. 1. Investment. 



B. Operating expenses. 



2. Administration. 



A. Fixed Charges. — These include under (1) interest on the investment, generally taken as 
5 per cent; taxes 1 to 1.5 per cent; insurance .5 per cent; depreciation, a varying amount depend- 
ing upon the life of the apparatus and maintenance or ordinary repairs, frequently taken as 2.5 
per cent. The maintenance is sometimes charged against operating expense. 

Under (2) such items as salaries of officers, clerks, stenographers, etc. not connected with the 
operating end. Office rent and office supplies are included. 

B. Operating Expenses. — This includes coal, oil, water, supplies for boiler and turbine room 
and labor. 

The life of the different items making up the Equipment of a Power Plant may be taken from 
the following table: 



LIFE OF APPARATUS 



Belts 

Boilers, Fire Tubes .... 

Boilers, Water Tubes . ... 

Breeching Steel ..... 

Buildings; Brick, Concrete, Steel Concrete 
Coal Bunkers ..... 

Coal conveyors — rectangular, bucket 
Coal Conveyor; Belt .... 

Cranes ...... 

Chimneys, brick .... 

Chimneys, steel, self-supporting 

Chimneys, steel guyed 

Economizers ..... 



Years 

7 
15 
25 
10 
50 
14 

8 
10 
25 
50 
20 
10 
20 



NOTES ON POWER PLANT DESIGN 



133 



Engines: Corliss 

Engines: High speed . 

Feed pumps, turbine centrifugal 

Feed pumps, plunger 

Generators, D. C. . . 

Generators, A. C. 

Heaters, open type . 

Heaters, closed type 

Motors .... 

Motor generator sets 

Piping 

Steel Flues 

Stokers 

Switchboard 

Turbines 

Wiring 



25 
15 
15 
12 
20 
25 
20 
10 
20 
15 
15 
10 
7 
25 
15 
20 



DEPRECIATION 

If the life of a piece of apparatus is known to be 20 years, that is to say, at the end of 20 years 
the apparatus is considered worthless and its value as junk is enough to pay for its removal, then 
each year a certain amount of money should be put by as a sinking fund so that at the end of the 
20th year, this money shall have accumulated to a sum sufficient to replace the apparatus. 

Evidently if the money put away did not draw interest, 5 per cent of the original cost would 
be added to the sinking fund each year; if however, the money drew 43^ per cent interest, com- 
pounded annually, the amount to be laid by each year would be 3.19 per cent of the first cost of 
the apparatus as is found by reference to the "interest table" which follows: 

lOOR 
This table has been calculated by means of the formula X = q , ^\n _ ^ 

X = rate of depreciation expressed in per cent of first cost. 

R - rate of interest received, compounded annually ; expressed as a decimal. 

n = years of life of apparatus. 

S = first cost of apparatus. 



This formula may be deduced thus : 



X 



The amount of money laid by each year is -tkt^S 

There has accumulated then 

X 

at the end of the first year -jr^S 

X X 

at the end of the second year -txptS {1 + R) + -TKrrS 

at the end of the third year -^S (1 + Rf + -^S (1 + i?) + -^S 



at the end of the fourth year -^S (1 + R)^ + -~^S (1 + Rf + -~^S {1 + R) + -~-S 



134 NOTES ON POWER PLANT DESIGN 

at the end of the nth year -^S (1 + RTK . . .-^S (1 + Rf + -^S {I + R) + -^S 

This summation should equal S. 
Equating and solving for X. 

X = 



100 



(1 + i?)-l + . . . (1 + i?)2 + (1 + i?) +1 

X°- 1 



The summation of a series Z"'^ . . . X^ + X + 1 = 



hence X = 



X - 1 
100 (1 + i?) - 1 lOOi? 



(1 + i?)° - 1 (1 + RY - 1 



RATE OF DEPRECIATION 
(Per Cent of First Cost) 

Rate of Interest, Per Cent. 
3.5 4 4.5 5 5.5 



5 


18.83 


18.65 


18.46 


18.28 


18.10 


17.91 


17.73 


17.40 


17.04 


6 


15.46 


15.26 


15.08 


14.89 


14.70 


14.52 


14.33 


13.97 


13.63 


7 


13.05 


12.85 


12.66 


12.46 


12.28 


12.09 


11.91 


11.15 


11.20 


8 


11.24 


11.05 


10.85 


10.66 


10.47 


10.28 


10.10 


9.74 


9.40 


9 


9.84 


9.64 


9.45 


9.26 


9.07 


8.88 


8.70 


8.34 


8.00 


10 


8.72 


8.52 


8.33 


8.14 


7.95 


7.76 


7.58 


7.23 


6.90 


11 


7.80 


7.61 


7.41 


7.22 


7.04 


6.85 


6.68 


6.33 


6.00 


12 


7.04 


6.85 


6.65 


6.46 


6.28 


6.10 


5.92 


5.60 


5.27 


13 


6.40 


6.20 


6.01 


5.83 


5.64 


5.47 


5.29 


4.96 


4.65 


14 


5.85 


5.65 


5.46 


5.28 


5.10 


4.93 


4.75 


4.49 


4.13 


15. 


5.37 


5.18 


4.99 


4.81 


4.63 


4.46 


4.29 


3.97 


3.66 


16 


4.96 


4.77 


4.58 


4.40 


4.22 


4.06 


3.89 


3.58 


3.30 


17 


4.59 


4.40 


4.22 


4.04 


3.87 


3.70 


3.54 


3.24 


2.96 


18 


4.27 


4.08 


3.90 


3.72 


3.55 


3.39 


3.23 


2.94 


2.66 


19 


3.98 


3.79 


3.61 


3.44 


3.27 


3.11 


2.96 


2.67 


2.47 


20 


3.72 


3.53 


3.36 


3.19 


3.02 


2.87 


2.71 


2.44 


2.18 


25 


2.74 


2.56 


2.40 


2.24 


2.09 


1.95 


1.82 


1.58 


1.36 


30 


2.10 


1.93 


1.78 


1.64 


1.50- 


1.38 


1.26 


1.06 


0.88 


35 


1.65 


1.50 


1.36 


1.23 


1.10 


0.99 


0.89 


0.72 


0.58 


40 


1.32 


1.18 


1.05 


0.93 


0.83 


0.73 


0.64 


0.50 


0.38 


45 


1.07 


0.94 


0.82 


0.72 


0.62 


0.54 


0.47 


0.35 


0.26 


50 


0.88 


0.76 


0.65 


0.56 


0.42 


0.40 


0.34 


0.25 


0.17 



Assumed useM life of apparatus at left of column. 

The continuous expense based upon the original cost of the plant is sometimes taken as 14 
per cent per year divided as follows :• interest 5 per cent; depreciation 5 per cent, repairs 2^/^ per 
cent, insurance 3^ per cent and taxes 1 per cent. 



NOTES ON POWER PLANT DESIGN 



135 



OPERATING COSTS IN CENTS PER K. W. HOUR FOR CERTAIN CENTRAL STATIONS 

IN MASSACHUSETTS 



Coal 


.462 


.710 


.618 


.690 


.703 


.565 


.635 


.880 


.740 


.650 


.740 


Wages 


.192 


.262 


.296 


.347 


.360 


.320 


.342 


.538 


.308 


.285 


.410 


Oil, Waste, etc 


.008 


.009 


.012 


.019 


.027 


.020 


.017 


.032 


.015 


.019 


.025 


Water 


.024 


.008 


.040 


.055 


.034 


.045 


.032 


.012 


.025 


.003 


.027 


Station Repairs, Bldgs. 


.015 


.020 


.052 


.021 


.012 


.023 


.035 


.012 


.017 


.063 


.034 


Steam Equipment Repairs 


.042 


.020 


.147 


.059 


.055 


.072 


.072 


.037 


.041 


.073 


.158 


Electrical Equipment Repairs. 


, .056 


.009 


.045 


.046 


.055 


.014 


.014 


.029 


.072 


.019 


.011 


Miscellaneous 


.023 


.022 


.000 


.000 


.000 


.021 


.033 


.080 


.024 


.040 


.000 


Total 


.822 


1.060 


1.210 


1.237 


1.246 


1.080 


1.180 


1.620 


1.242 


1.152 


1.412 


Coal per ton $ . . . , 


, 3.99 


4.75 


3.60 


4.40 


4.79 


3.78 


4.49 


4.68 


4.52 


3.97 


4.51 


K. W. Hours 
























Output 


88.5 


9.4 


8.7 


6.0 


5.4 


4.7 


4.6 


4.0 


4.0 


3.7 


3.1 



1,000,000 



BOSTON ELEVATED RAILWAY COMPANY 



Year 

Rated capacity 38,470 

Yearly load factor 

Cost of coal per K. W. hour, cents 

Labor plus labor on repairs per K. W. hour, cents 

Coal and all supplies per K. W. hour, cents .... 



Total per K. W. hour, cents 
Cost of coal per ton $ 



1906 


1908 


1910 


1912 


38,470 


50,425 


51,163 


61,350 


43 


37 


41.5 


36.4 


.47 


.56 


.48 


.41 


.17 


.21 


.17 


.17 


.60 


.86 


.58 


.52 


.77 


1.07 


.75 


.69 


3.186 


3.568 


3.283 


3.202 



OPERATING COSTS, COSTS IN CENTS PER K. W. HOUR 

Tyfical British Electric Light and Power Plants — 1902 

(From Engineering Record — March, 1904) 



K.W. 


Yearly Coal 


Oil, waste 


Wages 


Repairs 


Total 


installed 


load 
. factor 
per cent 


and 
Supplies 








6380 


20.93 .52 


.10 


.16 


.26 


1.04 


8740 


12.31 .56 


.06 


.34 


.28 


1.24 


1340 


17.84 .52 


.06 


.34 


.38 


1.30 


10477 


14.75 .68 


.08 


.18 


.36 


1.30 


3700 


18.87 .70 


.12 


.30 


.20 


1.32 


850 


28.44 .82 


.06 


.30 


.22 


1.40 


21190 


25.11 .74 


.12 


.30 


.26 


1.42 


1600 


15.82 .74 


.08 


.40 


.30 


1.52 


5642 


12.97 .92 


.20 


.32 


.18 


1.62 


1920 


13.31 .72 


.12 


.36 


.46 


1.66 


610 


14.54 .92 


.20 


.36 


" .22 


1.70 


990 


19.79 1.10 


.08 


.42 


.18 


1.78 


TOTAL COST IN DOLLARS OF A H. P. FOR A YEAH ON 10 HOUR BASIS 


Size of Plant 




Maximum Cost 






Minimum Cost 


H.P. 




per H. P. 






per H. P. 


2000 . 




24 






21 


1500 . 




26 






21 


1200 




30 






22 


1000- . 




33 






24 


800 . 




38 






26 


600 . 




46 






28 


500 




60 






31 


400 . 




57 






33 


300 . 




65 






38 


200 . 




77 






45 


100 




96 






60 


50 . 




110 






80 


25 . 


. 


130 






110 



136 



NOTES ON POWER PLANT DESIGN 



DISTRIBUTION OF OPERATING COSTS 

The operating cost per K. W. hour varies from less than one cent in the large plants to three 
and one-half cents in the small plants. Plants of from 2000 to 5000 K. W. capacity would operate 
(between one and one-half and one and one-tenth cents. 

The cost is distributed about as follows : 



Coal . 

Wages . 

Oil and waste, etc. 

Water . 

Station Repairs, Bldgs. 

Steam Equipment Repairs 

Electrical Equipment Repairs 



Per Cent 

56.0 

28.0 
2.0 
2.0 
1.6 
6.3 
4.1 



100.0 



A certain station of 10,000 K. W. rated capacity cost $100 per K. W. This cost was divided 
as follows: Buildings $20, Machinery $80. Charging 14 per cent on machinery and 7.5 per cent 
on buildings gives for fixed charges, 

.075 X 200,000 = 15,000 
.14 X 800,000 = 112,000 



127,000 



Suppose the yearly load factor is 18 per cent and that the total operatuig cost per K. W. hour, 
is 1.121 cents. 

The total output in K. W. hours for the year is 

8760 X 10,000 X .18 = 15,768,000 
$127000 - 15,768,000 

gives the overhead charge per K. W. hour to be added to the operating cost. This figures as .804 
cents. 

.804 + 1.12= 1.925 cents. 

It is evident that the higher the load factor the less the overhead to be added per K. W. to 
operating cost. 



COST OF STEAM POWER — (Small Units) 

Size of plant in H. P. 

Cost of plant per H. P. . 

Fixed charge, 14 per cent ....... 

Coal per H. P. hour, in pounds ...... 

Cost of coal at $5 per ton ....... 

Attendance, 3080 hours ........ 

Oil, waste and supplies ........ 

Cost 1 H. P. per annum, 10-hour basis $279.00 

Cost of 1 H. P. per hour $0.0906 



6 


10 


20 


$250.00 


$220.00 


$200.00 


$35.00 


$30.80 


$28.00 


20 


15 


12 


$154.00 
75.00 
15.00 


$103.00 
50.00 
10.00 


$82.50 

30.00 

6.00 



$194.80 
$0.0832 



$146.50 
$0.0475 



NOTES ON POWER PLANT DESIGN 



137 



COST OF GASOLENE POWER — Small Units 



Engineering News, Aug. 15, 1907. 



Size of plant in H. P. 
Price of engine in place . 
Gasolene per B. H. P. per hour 
Cost per gallon 

Cost per 3,080 hours 

Attendance at $1 per day 
Interest, 5 per cent 
Depreciation, 5 per cent 
Repairs, 10 per cent 
Supplies, 20 per cent 
Insurance, 2 per cent 
Taxes, 1 per cent 

Power Cost 



2 


6 


10 


20 


$150.00 


$325.00 


$500.00 


$750.00 


. . . Hgal. 


Mgal. 


3^ gal. 


Hgal. 


$0.22 


$0.20 


$0.19 


$0.18 


$451.53 


$924.00 


$975.13 


$1386.00 


308.00 


308.00 


308.00 


308.00 


7.50 


16.25 


25.00 


37.50 


7.50 


16.25 


25.00 


37.50 


15.00 


32.50 


50.00 


75.00 


30.00 


65.00 


100.00 


150.00 


3.00 


6.50 


10.00 


15.00 


1.50 


3.25 


5.00 


7.50 



$825.03 



$1371.75 



$1498.13 



$2016.50 



To these figures should be added charges on space occupied as follows: 
Value of space occupied ..... $100.00 

Interest, 5 per cent ...... 

Repairs, 2 per cent . . 

Insurance, 1 per cent ...... 

Taxes, 1 per cent ...... 



Total annual charge for space 

Total cost per annum .... 
Cost of 1 H. P. per annum, 10 hour basis 
Cost of 1 H. P. per hour 



$833.03 

416.51 

$0.1352 



$150.00 



$200.00 



$1385.25 

239.87 

$0.0780 



$1516.13 

151.61 

$0.0492 



$300.00 



$5.00 
2.00 
1.00 
1.00 


$7.50 
3.00 
1.50 
1.50 


$10.00 
4.00 
2.00 
2.00 


$15.00 
6.00 
3.00 
3.00 


$9.00 


$13.50 


$18.00 


$27.00 



$2043.30 

102.17 

$0.0331 



COST OF GAS POWER — Small Units 



.50 per 1000 cubic feet of gas less 20 per cent, if paid in 10 days = $1.20 net, gas 760 B. T. U. 
Size of plant in H. P. 

Engine cost in place 

Gas per H. P. hour in cu. ft. 



Value of gas consumed, 3080 hours 
Attendance, $1 per day 
Interest, 5 per cent 
Depreciation, 5 per cent 
Repairs, 10 per cent 
Supplies, 20 per cent 
Insurance, 2 per cent 
Taxes, 1 per cent 

Power cost 

Annual charge for space 



Total cost per annum . 

Cost of 1 H. P. per aimum, 10 hour basis 

Cost of 1 H.P. per hour . . 



2 


6 


10 


20 


$200.00 


$375.00 


$550.00 


$1050.00 


30 


25 


22 


20 



$221.76 


$554.40 


$843.12 


$1478.00 


308.00 


308.00 


308.00 


308.00 


10.00 


18.75 


27.50 


52.50 


10.00 


18.75 


27.50 


52.50 


30.00- 


37.50 


55.00 


105.00 


40.00 


75.00 


110.00 


210.00 


4.00 


7.50 


11.00 


21.00 


2.00 


3.75 


5.50 


10.50 



$615.76 
9.00 



$624.76 

312.38 

$0.1014 



$1023.65 
13.50 



$1387.62 
18.00 



$1037.15 

172.86 

$0.0561 



$1405.62 

110.56 

$0.0456 



$2237.50 
27.00 



$2264.50 
143.22 
$0.0367 



138 NOTES ON POWER PLANT DESIGN 

GUARANTEES 

It is customary to ask that contractors, when submitting a bid for prime movers or for power- 
driven machinery, give a guarantee as to the performance or efficiency of the equipment they pro- 
pose to furnish. 

This guarantee may in the case of a steam engine be based on povmds of steam per I. H. P. 
or per K. W. hour at rated load which should be specified, as should also the pressure and con- 
dition of the steam at the throttle and the temperature of the cold condensing water. 

The steam consumption at half load and at twenty-five per cent overload may also be given 
and included in the guarantee. 

The performance of large pumping engines is stated in figures representing the "duty" or 
foot pounds of water work done per 1,000,000 B. T. U. or per 1000 lbs. of steam of quality and 
pressure specified. 

The performance of centrifugal pumping units when motor driven is often given in overall 
mechanical efficiency of pump and motor when working at stated conditions as to head and capacity. 

In contracts containing a guarantee as to performance, provision is made for deducting from 
the first cost ot the apparatus a fixed amount for each fraction of a pound the engine or turbine 
exceeds the consumption mentioned in the guarantee; similarly in the case of a high duty pumping 
engine a deduction is made for each million duty under that guaranteed. 

It is not necessary that there be a "bonus" for a performance better than that guaranteed. 

The deduction made from the original price in case of a failure to meet the guarantee is in no 
way to be in the nature of a penalty. It must be that amount which the purchaser would lose in 
money and accrued interest during the life of the apparatus through the less efficient performance 
than that guaranteed. 

For example, a certain contractor guaranteed a steam consumption per I. H. P, hour on an 
engine and condenser and failed to meet his guarantee. 

The contract read that should the steam consumption per I. H. P. at full load, namely 2000 
I. H. P., exceed 13.7 lbs. per I. H. P. hour a deduction is to be made from the original contract 
price at the rate of $4400 per 1/10 lb. that the actual performance exceeds the guaranteed steam 
consumption, provided the steam consumption does not exceed that guaranteed by as much as 
3/10 of a pound. Should the steam consumption at full load exceed that guaranteed by 3/10 of 
a pound or more, the purchaser could at his option reject the engine. 

The figure $4400 was arrived at in this way : 

The life of the engine may be taken as 18 years and it may be assiuned to run 3000 hours per 
year with full load in this case. The extra steam per hour per 1/10 lb. in excess of guarantee is 
per year .1 x 2000 x 3000 = 600,000 lbs. for engine alone. Adding 10% of this as the extra steam 
used by the auxiliaries makes 660,000 lbs. Assuming 9.5 lbs. actual evaporation per lb. of coal 
makes the extra coal per year 69,474 lbs. or 34.74 tons. With coal at $4.50 per ton this figures 
$156.33. 

If money draws 5 per cent interest, the loss at the end of 18 years may be figured as follows: 

End of first year, 156.33 

End of second year, 1.05x156.33 + 156.33 

End of third year, 1.05 x 156.33 + 1.05 x 156.33 -1- 156.33 

End of fourth year, 1 . 05*x 156.33 + 1 . 05^x 156.33 + 1.05 x 156.33 + 156.33 

End of 18th year, 1.051^ x 156.33 + 1.05i« x 156.33 + 1.05 X 156.33 + 156.33 

= $4402.25 
If R is taken as the rate of interest; n = number of years and- the loss for the first year is $1. 
This may be written: 

1 — Cl 4- R)^ 
1+ (l+i?) + (l + i?)2 + (i+i?)3 + (l+i?)-i = l-\l+R) 

which may be put into this form q , ^\n _ j 

R 



NOTES ON POWER PLANT DESIGN 139 

One dollar lost each year plus the interest which would have accrued would at the end of n 

(1 + i?)° — 1 
years amount to -^ ^ which is the "annuity value of one dollar." 

In the case just considered this gives 
(1 + .05)18 - 1 



.05 



= 28.16 28.16 X 156.33 = $4402.25 



A guarantee on the duty of a 12,000,000 gallon pump read as follows: "With steam at the 
throttle of 150 lbs. gage pressure and containing not over IJ^ per cent moisture, the pump is guaran- 
teed when pumping 12,000,000 U. S. gallons in 24 hours against a total head of 200 feet to give 
a duty of 140,000,000 per 1000 lbs. of steam." 

"Should the pump fail to make the duty guaranteed an amount representing the monetary 
loss suffered by the city in a period of 20 years, takeft as the life of the pimap, is to be deducted 
from the original contract price of the pump." 

"The amount to be deducted per 1,000,000 loss of duty as calculated and mutually agreed 
upon by engineers representing the city and the contractor is $2116.41." 

"The extra cost of coal per year per million loss of duty, figured on coal at $4.60 a ton with 
an evaporation of 10 lbs. of water per pound of coal and on the basis that the pump runs only 
90 per cent of the year and that it runs at 5/6 of its rated capacity is $63.94." 

The annuity value of $1 for 20 years a?b 5 per cent is $33.1. 

63.94 X 33.1 = $2116.41. 
The calculations are outlined below: , 

365. X .9 = 328.5 days 
12,000,000 X 5/6 = 10,000,000 gals, per 24 hours. 

328.5 X 10,000,000 X 8.33 x 200 = ft. lbs. per year. 





Ft. lbs. per year 
140,000,000 


steam used per year ^^ 

1000 - "^^ 


,092 (A) 






Ft. lbs. per year 
139,000,000 


steam used per year oqq^a m\ 
1000 = "^^^^^ ^^^ 




B 
A 


Steam per year 
39,370,000 
39,092,000 


Coal per year, lbs. 
3,937,000 
3,909,200 


^ 


Coal per year, tons 
1968.5 
1954.6 




13.9 




13.9 X 4.60 = $63.94 
63.94 X 33.1 = $2116.41 







140 NOTES ON POWER PLANT DESIGN 



PIPING 



Steel pipe is cheaper than wrought iron pipe and is generally furnished when an order is given 
for pipe unless wrought iron pipe is specifically called for. 

There are two weights of pipe in addition to the Extra Strong and Double Extra Strong one 
known as "Merchant," and the other known as "Card" or "Full Weight" pipe. 

The term "Standard" or "Merchant," is used to describe a pipe not "Card" or "Full Weight." 

For many purposes this lighter weight is just as good as the "Full Weight." 

The term "Card" or "Full Weight" refers to a pipe of weights as given in the table which 
follows. 

Pipe in sizes up to and including 12" refers to inside dia. Above 12" the pipe is rated by the 
outside dia. 

Pipe comes in lengths of from 18 ft. to 21 ft. and in figuring the cost of a system of piping 
there is some waste pipe which must be taken account of. 

Pages 141 to 154 are taken from the catalogue of the Walworth Mfg. Co. The discounts 
vary from time to time but may be assumed as being approximately correct. 

The coefficient of expansion of steel piping is .0000065 or in other words, a pipe expands .0000065 
its length per degree F. 

The expansion on high pressure work is taken care of by expansion bends similar to those 
shown on the plot (page 155). 

The amount of motion such bends will provide for has been determined experimentally by 
the Crane Company. The results of this work were published in the Valve World of October, 
1915. This plot is reproduced from that paper. 

If the total expansion to be taken up by a double offset or U bend is 5" in general, the bend 
or offset would be sprung apart one-half the expansion, or in this case 2^/^" when the pipe was 
erected. By this means the expansion first relieves the stress, then puts into the pipe a stress of 
the opposite kind but of equal amount. 

Much of the high pressure piping put up to-day has outlets, taking the place of cast tees, 
welded to the pipe. This saves joints and thereby reduces the trouble from leaky gaskets. 

The labor cost of the erection of piping depends upon the design of the system; in general 
however, for the ordinary power house the cost varies from 15 per cent to 25 per cent of the first 
cost of the fabricated material; 15 per cent would be considered a low cost; 20 per cent about an 
average value. 

Card or Full Weight pipe is generally used for pressures carried in power plants. 

The discount on card or Full Weight is 68 per cent. The discount on Extra Strong 62 per 
cent; on Double Extra Strong 45 per cent. 



NOTES ON POWER PLANT DESIGN 



141 



PRICE LIST OF 

WROUGHT IRON AND STEEL PIPE. 



Nominal 

Inside 
Diameter. 


STANDARD. 1 EXTRA STRONG. I DOUBLE EXTRA STRONG. | 


Price 
Per Foot. 


Nominal 
Weight 
Per Foot. 


Price 
Per Foot. 


Nominal 
Weight 
Per Foot. 


Price 
Per Foot. 


Nominal 
Weight 
Per Foot. 


i,s 


.05y2 


0.24 


.11 


0.29 






% 


.OSVa 


0.42 


11 


0.54 






% 1 .051/2 


0.56 


11 


0.74 


.25 


96 


1/2 I .081/2 


0.85 


.12 


1.09 


.25 


1.70 


% 


.111/2 


1.12 


15 


1.39 


.30 


2.44 


1 


.levs 


1.67 


.22 


2.17 


.37 


3.65 


l',4 


.221/3 


2.24 


.30 


3.00 


.52 


5.20 


11/2 


.27 2.68 


.36 


3.63 


65 


6.40 


2- 


.36 3.61 


.50 


5.02 


95 


9.02 


21/2 


.571/2 


5.74 


.81 


7.67 


1.37 


13.68 


3 


.751/2 


7.54 


1.05 


10.25 


1.92 


18.56 


31,4 


.95 


9.00 


1.33 


12.47 


2.45 


22.75 


4 


1.08 


10.66 


1.50 


14.97 


2.85 


27.48 


4V2 


1.30 


12.49 


1.95 


18.22 


3.30 


32.53 


5 


1.45 


14.50 


2.16 


20.54 


3.80 


38.12 


6 


1.88 


18.76 


2.90 


28.58 


5.30 


53.11 


7 


2.35 


23.27 


3.80 


37.67 


6.25 


62.38 


8 


2.50 


25.00 










8 


2.82 


28.18 


4.30 


43.00 


7.20 


71.62 


9 


3.40 


33.70 


5.00 


48.73 






10 


3.50 


35.00 










10 


4.00 


40.00 


5.50 


54.74 






12 


4.50 


45.00 


6.50 


65.42 






. 12 


4.90 


49.00 









On orders for 8-incli, 10-inch, 12-inch pipe we will ship 8-inch, 25 lb.. 10-inch, 35 lb., 12-inch, 45 lb., 
Unless otherwise specified. Customers should, however, always indicate which weight is wanted. 

When Standard Pipe is ordered, black pipe, random lengths, with threads and couplings, will be shipped^ 
unless otherwise specified. 

For pipe smoothed on the inside, known as plugged and reamed, an extra charge will be made above 
regular pipe. 

Extra Strong and Double Extra Strong Pipe will be shipped in random lengths and plain ends, unless 
otherwise ordered. For this pipe, fitted with threads and couplings, an extra charge will be made above 
regular. For cut lengths of any pipe, an extra charge will be made above random lengths. For galvanized 
or asphalted pipe, an extra charge will be made above black. 

For Price List for Cutting and Threading, see page 79. 



GALVANIZED FLANGED FITTINGS. 

Faced and Drilled. 



Size. 
Inches. 


90" Elbows. 
Galvanized 


45" Elbows. 
Galvanized. 


Tees. 
Galvanized. 


Reducing Tees. 
Galvanized. 


Crosses. 
Galvanized. 


Y-Branches. 
Galvanized. 


3 


2.80 


2.35 


4.40 


4.75 


5.85 


, 


4 


4.00 


3.70 


6.40 


7.00 


9.70 


9.90 


5 


5.50 


4.90 


8.00 


8.80 


12.00 


12.60 


6 


6.40 


5.50 


9.20 


9.80 


13.50 


16.50 


7 


8.00 


6.00 


11.20 


12.00 


19.00 


18.70 


8 


12.^0 


9.50 


18.00 


19.00 


31.00 


27.00 


9 


17.00 


14.00 


22.50 


24.00 


40.00 


37.50 


10 


19.20 


15.00 


26.00 


28.00 


50.00 


50.00 


12 


26.60 


22.00 


41.00 


44.00 


72.00 


71.00 


14 


41.70 


24.00 


61.00 


66.00 


86.00 


100.00 


15 


53.00 


30.00 


76.00 


82.00 


108.00 


116.00 


16 


76.00 


49.00 


113.50 


122.00 


138.00 


168.00 


18 


91.00 


70.00 


148.00 


159.00 


174.00 


191.00 


20 


120.00 


84.00 


157.00 


168.00 


197.00 


208.00 


22 


142.00 


100.00 


206.00 


222.00 


260.00 


266.00 


24 


178.00 


122.00 


253.00 


272.00 


325.00 


336.00 



The above list is for fittings drilled in accordance with SPIRAL PIPE STANDARD. 
These fittings are also furnished flanged and drilled in accordance with A. S. M. E., Standard at an 
additional cost. 

Base elbows for supporting vertical runs furnished as ordered. 



SPIRAL RIVETED GALVANIZED PRESSURE PIPE. 

Lengths up to 20 Feet. 



Size. 
Inches. 


U.S. 
Standard 
Gauge. 


Per Foot. 
Galvanized. 
No Flanges. 


* Flanges 

Attached. 

Each. 


** Diameter 
Flanges. 
Inches. 


Bolt 
Circle. 
Inches. 


No. 

of 

Bolts. 


Size 
Bolts. 
Inches. 


3 1 20 1 .474 


1.90 


6 


4% 


4 


Vie 


4 


18 1 .680 


2.30 


7 


51=/l6 


8 


yi6 


5 


18 1 .826 


2.70 


8 


6'yio 


8 


'/,<, 


6 


16 


1.04 


3.15 


9 


Vk 


8 


1/2 


7 


16 


1.216 


3.40 


10 


9 


8 1/2 1 


8 


16 


1.395 


4.05 


11 


10 


8 


1/2 


9 


16 


1.564 


4.90 


13 ' 


HI/4 


8 


li. 


10 


16 


1.731 1 5.45 


14 


12Vi 1 8 


1/2 


12 16 


2.067 1 5.85 


16 


141/4 1 12 


1/2 


14 14 


2.91 1 6.80 


18 


16U 12 


1/2 


15 


14 


3.12 


9.35 


19 


17-/1 12 


1/' 


16 


14 


3.33 


11.00 


2114 


19'/4 


12 


y2 


18 


14 


3.66 


13.35 


231/4 


211/t 


16 


% 


20 


14 


4.06 1 15.85 


251/4 1 23i,'8 


16 


% 


22 


12 


5.91 1 20.25 


281/4 


26 


16 


% 


24 


12 1 6.41 1 22.70 


30, 


27% 


16 


% 



•Flanges Drilled. 
■•■•Spiral Pipe Diameters. 



Additional price charged for A. S. M. E. Standard Diameters. 



The discount on Spiral Riveted pipe is 403per cent, 
iron or flanged fittings. 



Galvanized fittings cost 15 per cent, more than the net price of ordinary cast 



142 



NOTES ON POWER PLANT DESIGN 



TABLE OF DIMENSIONS OF 

*CARD OR FULL WEIGHT WROUGHT IRON OR 

STEEL PIPE. 

Foir Steam, Water and Gas. 



Nomi- 
nal 
Inside 
Diam. 
Ins. 


Actual 
Outside 
Diameter. 
lnche.s. 


Approx. 

Inside 
Diameter. 

Inches. 


Approx. 
Thick- 
ness. 
Inches. 


Length of 
Pipe per 

Sq. Ft. of 

Outside 

Surface. 

Feet 


Inside 
Area. 
Inches. 


Length of 
Pipe Con- 
taining 

One 
Cu. Ft. 
Feet. 


••Nomi. 

nal 
Weight 
per Ft 
Pounds. 


No. of 

Threads 

per Inch 

of 

Saew. 


Contents 
in 

•*»Gals. 
per Ft. 


Vs 


.405 


.270 


.068 


9.44 


.0568 


2513. 


.24 


27 


.0006 


Vi 


.54 


.364 


.088 


7.075 


.1041 


1383.3 


.42 


18 


.0026 


% 


.675 


.494 


.091 


5.657 


.1909 


751.5 


.56 


18 


.0057 


V2 


.84 


.623 


.109 


4.547 


.3039 


472.4 


.85 


14 


.0102 


% 


1.05 


.824 


.113 


3.637 


.5333 


270. 


1.12 


14 


.0230 


1 


1.315 


1.048 


.134 


2.903 


.8609 


166.9 


1.67 


IIV2 


.0408 


1% 


1.66 


1.380 


.140 


2.301 


1.496 


96.25 


2.24 


IIV2 


.0638 


iy2 


1.90 


1.611 


.145 


2.010 


2.038 


70.65 


2.68 


IIV2 


.0918 


2 


2.375 


2.067 


.154 


1.608 


3.355 


42.91 


3.61 


IIV2 


.1632 


2;^ 


2.875 


2.468 


.204 


1.328 


4.780 


30.11 


5.74 


8 


.2550 


3 


3.50 


3.067 


.217 


1.091 


7.388 


19.49 


7.54 


8 


.3673 


3V2 


4.00 


3.548 


.226 


.955 


9.887 


14.56 


9.00 


8 


.4998 


4 


4.50 


4.026 


.237 


.849 


12.730 


11.31 


10.66 


8 


.6528 


4^2 


5.00 


4.508 


.246 


.765 


15.961 


9.03 


12.49 


8 


.8263 


5 


5.563 


5.045 


.259 


.687 


19.985 


7.20 


14.50 


8 


1.020 


6 


6.625 


6.065 


.280 


.577 


28.886 


4.98 


18.76 


8 


1.469 


7 


7.625 


7.023 


.301 


.501 


38.743 


3.72 


23.27 


8 


1.999 


8 


8.625 


7.982 


.322 


.444 


50.021 


2.88 


28.18 


8 


2.6U 


9 


9.625 


8.937 


.344 


.397 


62.722 


2.29 


33.70 


8 


3.300 


10 


10.75 


10.019 


.366 


.355 


78.822 


1.82 


40.00 


8 


4.081 


12 


12.75 


12.000 


.375 


.299 


113.098 


1.270 


49.00 


8 


5.87 



"MERCHANT WEIGHT" WROUGHT IRON OR 
STEEL PIPE. 

8-INCH, lO-mCH, 12-INCH SIZES. 



Nomi- 
nal 
Inside 
Diam. 
Ins. 


Actual 
Outside 
Diameter. 
Inches. 


Approx. 

Inside 
Diameter. 

Inches. 


Approx. 
Thick- 
ness. 
Inches. 


Length of 
Pipe per 

Sq. Ft. of 

Outside 

Surface. 

Feet. 


Inside 
Area. 
Inches. 


Length of 
Pipe Con- 
taining 

One 
Cu. Ft. 
Feet. 


**Nomi- 

nal 
Weight 
per Ft 
Pounds. 


No. of 

Threads 

per Inch 

of 

Screw. 


Contents 

in 
"'Gals, 
per Ft 


8 1 8.625 1 8.073 .276 | .444 | 51.187] 2.81 | 25.00 | 8 | 2.659 


10 1 10.750 1 10.138 .306 .355 | 80.715 1 1.78 35.00 | 8 | 4.190 


12 1 12.750 1 12.094 | .328 .299 1 114.875 1 1.25 45.00 | 8 | 5.967 



*EXTRA STRONG WROUGHT IRON OR STEEL PIPE. 

_ . 


* DOUBLE EXTRA STRONG WROUGHT IRON OR 
STEEL PIPE. 


Nominal 
Inside 
Diam. 
Inches. 


Approx. Inside 

Diameter. 

Inches. 


Actual Outside 
Diameter, 
tnches. 


Approx. 

Thickness. 

Inches. 


Length of Rpe 

per 

Square Foot 

of Outside 

Surface. 

Feet 


Inside Area. 
Square Inches. 


**Nominal 

Weight per 

Foot 

Pounds. 




Nominal 
Inside 
Diam. 

Inches. 


Approx. Inside 

Diameter. 

Inches. 


Actual Outside 

Diameter. 

Inches. 


Approx. 

Thickness. 

Inches. 


Length of Pipe 

per 

Square Foot 

of Outside 

Surface. 

Feet 


Inside Area. 
Square Inches. 


**Nominal 

Weight per 

Foot 

Pounds. 


Vb 


.205 


.405 


.10 


9.433 


.033 


.29 


?'s 


.230 


.675 


220 


5.660 


.041 


.96 


Vi 


.294 


.54 


.123 


7.075 


.068 


.54 


% 


.421 


.675 


.127 


5.657 


.139 


.74 


% 


.244 


.84 


.298 


4.547 


.047 


1.70 


1/2 


.542 


.84 


.149 


4.547 


.231 


1.09 


% 


.422 


1.05 


314 


3.637 


.140 


2.44 


% 


.736 


1.05 


.157 


3.637 


.425 


1.39 


1 


.587 


1.315 


.364 


2.904 


.271 


3.65 


1 


.951 


1.315 


.182 


2.904 


.710 


2.17 


VA 


1.272 


1.66 


.194 


2.301 


1.271 


3.00 


VA 


.885 


1.66 


.388 


2.304 


.615 


5.20 . 


W2 


1.494 


1.90 


.203 


2.010 1 1.753 


3.63 


IV2 


1.088 


1.90 1 .406 


2.010 


.930 


6.40 


2 


1.933 


2.375 


.221 


1.608 1 2.935 


5.02 


2 


1.491 


2.375 


.442 


1.608 


1.744 


9.02 


2y2 


2.315 


2.875 


.280 


1.328 4.209 


7.67 


3 


2.892 


3.50 


.304 


1.091 1 6.569 


10.25 


2y2 


1.755 


2.875 


.560 


1.328 


2.419 


13.68 


3y2 


3.358 


4.00 


.321 


.955 8.856 


12.47 


3 


2.284 


3.50 


.608 


1.091 


4.097 


18.56 


4 


3.818 


4.50 


.341 


.849 1 11.449 


14.97 


SVa • 


2.716 


4.00 


.642 


.955 


5.794 


22.75 


4>/2 


4.280 


5.00 


.360 


.764 1 14.387 


18.22 


4 


3.136 1 4.50 1 .682 


.849 


7.724 


27.48 


5 


4.813 


5.563 


.375 


.687 1 18.193 


20.54 


6 


5.751 


6.625 


.437 


.577 1 25.976 


28.58 


4y2 


3.564 


5.00 


.718 


.764 


9.976 


32.53 


7 


6.625 


7.625 


.500 


.501 1 34.472 


37.67 


5 


4.063 


5.563 1 .75 


.687 


12.965 


38.12 


8' 1 7.625 


8.625 


.500 


.443 1 45.664 


43.00 


6 


4.875 


6.625 


.875 


.577 


18.665 


53.11 


9 1 8.62 


9.62 


.500 


.397 1 58.426 


48.25 


7 


5.875 1 7.625 


.875 


.501 


27.109 


62.38 


10 1 9.75 


10.75 


.500 


.355 74.662 


54.00 


12 1 11.75 


12.75 


.500 


.299 1 108.430 


65.00 


8 


6.875 


8.625 


.875 


.443 


37.122 


71.62 



NOTES ON POWER PLANT DESIGN 



143 



DIMENSIONS OF 

STANDARD WEIGHT 
CAST IRON SCREWED FITTINGS. 

For Steam Working Pressures up to 125 Lbs. 




11 i2_18 



81 32 



Size Inches 


% 


% 


Vs 


% 


1 


1% 


1^2 


2 


2y2 


3 


3y2 


4 


4y2 


5 


6 


7 


8 


9 


10 


12 


A-Center to Face.Inches 


% 


% 


IVio 


1%6 


iy2 


ll?i6 


2 


2% 


2ys 


'36A0 


3Hi6 


4 


4%6 


4iyi6 


55/10 


eyio 


6"A6 


7y2 


8y4 


9%«f 


AA-Face to Face.Inches 


IV2 


1% 


2^8 


2% 


3 


3% 


4 


4% 


5% 


6% 


7% 


8 


syg 


. 9% 


10% 


i2y8 


13% 


15 


i6y2 


i9y8 


B-Center to Face.Inches 


%c 


%G 


His 


i%o 


1%6 


IWe 


l?io 


1% 


1% 


lys 


2%6 


2y4 


2yi6 


2%e 


2i?ie 


3y8 


3%6 


3y8 


45/16 


478 


C-Center to Face.Inches 


... 


1%6 


1% 


2%6 


2y2 


3 


31,4 


4 


5 


5% 


6% 


7y8 


778- 


8^2 


91%6 


iiy* 


1215/10 


i4y2 


16 


— 


D-Face to Face.Inches 


... 


2IA0 


2%fl 


■ 2% 


3^4 


3% 


43/4 


SVa 


eme 


7% 


8% 


9% 


ioy2 


11%6 


isyg 


14% 


161%6 


19 


2oy8 


... 


X-Centerto Back 1 T„^t,oe 
of Thread.- r"<=h^ 


% 


Via 


%6 


% 


Ys 


lys 


1%6 


1^2 


m 


2%6 


2% 


2% 


3%8 


3yio 


3i%o 


4%6 


53/16 


5% 


6y2 


711/16 


Y-CentertoBack ( t„^^„, 
of Thread.. 1^"^^^ 


Via 


Vs 


%e 


1/4 


S/^6 


% 


% 


y2 


% 


% 


1 


lys 


1%6 


1%« 


l%e 


1% 


115^6 


2y8 


2%6 


3 


Z-CentertoBack / , ^. ^ 
of Thread., i^"^*^^ 


... 


1 


1% 


11/2 


1% 


25/ie 


2%6 


sys 


4 


4% 


5%6 


6 


6% 


7y4 


8%6 


9% 


115/8 


12% 


im 


— 



DIMENSIONS OF 

EXTRA HEAVY 
CAST IRON SCREW FITTINGS. 

For Steam Working Pressures to 250 Lbs. 





331 



332 




333 




334. 



Size . Inches 


y2 


% 


1 


iy4 


iy2 


2 


272 


3 


372 


4 


472 


5 


6 


... 


A-Center to Face Inches 


15/32 


1% 


11%2 


115A6 


2yi6 


272 


3 


31716 


4y32 


415/'32 


42732 


5732 


51 %6 


... 


AA-Face to Face Inches 


25/16 


2% 


3%6 


378 


478 


5 


6 


7% 


8%6 


816/16 


9i7i6 


lO^Ae 


115/8 


... 


B-Center to Face ■. Inches 


% 


Vs 


1 


1%6 


ly* 


iy2 


1% 


2% 


2%« 


21%6 


278 


378 


35A8 


... 


E-Outside Diameter of Bead—Inches 


12yS2 


1=^%2 


25/16 


2% 


3^6 


3% 


4%6 


5% 


6 


613A6 


7% 


715A6 


95A6 


— . 


F-Widthof Bead Inches 


%e 


y2 


%6 


1^6 


% 


78 


1 


17* 


15/le 


1%6 


19/16 


11%*^ 


-1% 


— . 


G-Thread Length Inches 


%6 


% 


11^6 


i%e 


% 


1 


178 


1% 


1%6 


1%.6 


11M6 


ll?l6 


178 





X-Centerto Back of Thread..Inches 


1%2 


% 


2%2 


lys 


15A6 


15/'8 


2 


25/18 


2^6 


27i6 


21%6 


3?l6 


315A6 





■Y-Center to Back of Thread.. Inches 


%6 


% 


5/16 


% 


% 


72 


% 




1 


178 


1%6 


15A6 


1%6 


... 



144 



NOTES ON POWER PLANT DESIGN 



STANDARD WEIGHT. 
CAST IRON SCREWED FITTINGS. 

125 Lbs. Working Pressure. 



STRAIGHT 
ELBOWS. 



REDUCING 
ELBOWS. 



Size ..Inches | Vi % 1/2 % 


1 


IVi 


11'2 


2 


21/2 1 3 




Size 


Inches | % V2 | % 


1 


VA 


IV2 1 2 21/2 3 1 3y2 


Fig. 11, R. H Eacli 1 .05 .05 .06 .08 


.101/2 


.16 


.20 


.28 


.50 .75 


Fig. 13-.__ - 


Each 1 .06 .07 | .09 


.12 


.18 


.23 1 .32 .60 .85 | 1.20 


R. H. Galvanized-_.Each .10 .10 .12 .16 


.21 


.32 


.40 


.56 


1.00 1 1.50 


Galvanized _.. 


Each 1 .12 .14 | .18 


^24 


.36 


.46 1 .64 1.20 1.70 2.40 


Fig.l2, R.andL._..Each .06 .06 .07 .09 


.12 


.18 


.23 


.32 


.60 .85 


Size 


_._. Inches | 4 41/2] 5 


6 


7 


8 9 10 12 i .-.- 


Size Inches | SVi 4 41/2 5 


6 


7 


8 


9 


10 1 12 


Fig. 13 


Each |l.40 2.00 1 2.30 


3.15 


5.40 


7.75 1 10.50 15.50 23.00 ___. 


Fig. 11, R. H Each 1 1.05 1.20 1.75 2.00 


2.75 


4.70 


6.75 


9.00 


13.50 20.00 


Galvanized ___ 


Each I2.8O 4.00 1 4.60 


6.30 


10.80 


15.50 1 21.00 31.00 1 46.00 1 .— 


R. H. Galvanized-. .Each | 2.10 2.40 3.50 4.00 


5.50 


9.40 


13.50 


18.00 


27.00 40.00 















For Elbows tapped left hand use Right and Left Elbow List. 

Ri^ht and Left Hand Elbows have ribs on the band of the end that is tapped left hand. 



ELBOWS 45°. 



SIDE OUTLET 
ELBOWS. 



Size 


.Inches 


',i 


% 


V2 


% 


1 


VA 


11/2 


2 


21/0 


3 


Fig. 21 _.__ 


...Each 


.06 


.06 


.07 


.10 


.12 


.19 


.24 


.34 


.60 


.90 


Galvanized- 


...Each 


.12 


.12 


.14 


.20 


.24 


.38 


.48 


.68 


1.20 


1.80 


Size 


.Inches 


3Vi 


4 


41/2 


5 


6 


7 


8 


9 


10 


12 


Fig.21_... 


...Each 


1.25 


1.45 


2.20 


2.50 


3.45 


5.90 


8.50 


11.25 


17.00 


25.00 


Galvanized. 


...Each 


2.50 


2.90 


4.40 


5,00 


6.90 


11.80 


17.00 


22.50 


34.00 


50.00 



Size 


..Inches 


V2 


% 


1 


1% 


W2 


2 


2V2 


3 1 


3% 


Fig. 22 


...Each 


.18 


.24 


.30 


.48 


.60 


.84 


1.50 


2.25 


3.15 


Galvanized. 


. ..Each 


.36 


.48 


.60 


.96 


1.20 


1.68 


3.00 


4.50 


6.30 


Size 


..Inches 


4 


4V2 


5 


6 


7 


8 


9 


10 


12 


Fig. 22 


...Each 


3.60 


5.25 


6.00 


8.25 


14.00 


20,00 


26.00 


40.00 


60.00 


Galvanized _ 


Each 


7.20 


10.50 


12.00 


16.50 


28.00 


40.00 


52.00 


80.00 


120.00 



STRAIGHT 
TEES. 



REDUCING 
TEES. 



Size 


..Inches 


% 


% 


1/2 


% 


1 


1% 


IJ/2 


2 


21/2 


3 ■: 


Size 


.Inches 


:<: 


V2 


% 


1 1 lU 


IV2 


2 


2'/2 


3 


3"2 


Fig.31__._ 


...Each 


.08 


.08 


.09 


.12 


.15 


.23 


.29 


.41 


.73 


1.10 


Fig. 32 .... 


- . . Each 


.09 


.10 


.14 


.17 1 .27 


.33 


.47 


.83 


1.25 1 


1.75 


Galvanized. 


...Each 


.16 


.16 


.18 


.24 


.30 


.46 


.58 


.82 


1.46 


2.20 


Galvanized. 


...Each 


.18 


.20 


.28 


.34 1 .54 


.66 


.94 


1.66 


2.50 


3.50 


Size 


..Inches 


3'/2 


4 


414 


5 


6 


7 


8 


9 


10 


12 


Size 


..Inches 


4 


41/2 


5 


6 1 7 


8 


9 


10 


12 




Fig. 31 .... 


...Each 


1.50 


1.75 


2.55 


3.00 


4.00 


6.80 


9.75 


13.00 


19.50 


29.00 


Fig. 32..... 


...Each 


2.00 


2.95 


3.50 


4.60 1 7.80 


11.25 


15.00 


22.50 


33.50 




Galvanized. 


...Each 


3.00 


3.50 


5.10 


6.00 


8-00 


13.60 


19.50 


26.00 


39.00 


58.00 


Galvanized 


...Each 


4.00 


5.90 


7.00 


9.20 Il5.60 


22.50 


30.00 


45.00 


67.00 





STRAIGHT 
SIZES. 



The largest opening of Reducing Fittings determines the list price. 

CROSSES. 

REDUCING 

SIZES. 



Size 


..Inches 


% 


V2 


% 


1 IVi 1 IV2 2 


21/2 


3 1 3'/2 


Size 


. Inches 


V' 


?i 


1 


1% 


11/2 


2 


21/2 


3 


•31/3 


Fig. 51.. . 


—Each 


.15 


.16 


.22 


.27 1 .42 1 .53 .75 


1.30 


2.00 1 2.70 


-Fig. 52 


...Each 


.18 


.25 


.30 


.46 


.60 


.83 


1.45 


2.20 


3,00 


Galvanized 


.. Each 


.30 


.32 


.44 


.54 1 .84 1.06 1.50 


2.60 


4.00 5.40 


Galvanized. 


Each 


.36 


.50 


.60 


.92 


1.20 


1.66 


2.90 


4.40 


6.00 


Size 


__ Inches 


4 


4Vi 


5 


6 1 7. 1 8 9 


10 


12 |._.. 


Size 


.-Inches 


4 


4V2 


5 


6 


7 


8 


9 


10 


12 


Fig. 51 


...Each 


3.15 


4.60 


5.50 


7.25 1 12.25 17.50 23.50 


35.00 


52.50|_... 


Fig. 52 


...Each 


3.50 


5.10 


6.00 


8.00 


13.50 


19.25 


26.00 


38.50 


58.00 


Galvanized . 


...Each 


6.30 


9.20 


11.00 


14.50 1 24.50 1 35.00 47.00 


70.00 


105.00|-..- 


Galvanized. 


...Each 


7.00 


10.20 


12.00 


16.00 


27.00 


38.50 


52.00 


77.00 


116.00 



REDUCING 
COUPLINGS. 

REGULAR PATTERN, 



The largest opening of Reccing Fittings determines the list price. 

ECCENTRIC 

REDUCING 

COUPLINGS. 



Size ...Inches 


2 


21/2 


3 


31/2 


4 


41/2 


5 


6 


7 


8 


9 


10 


12 


Fig. 61... Each 


.43 


.60 


.80 


1.00 


1.35 


1.85 


2.00 


2.70 


5.35 


6.75 


8.35 10.00 15.00 


Galvanized ... 


.86 


1.20 1.60 


2.00 


2.70 


3.70 


4.00 


5.40 


10.70 13.50 


16.70 20.00 30.00 



Size ...Inches 


1 


IVt 


V/2 


2 


2y2 


3 


3% 


4 


Fig. 62.. .Each 


-.50 


.55 


.72 


1.00 


1.50 


2.40 


3.00 


4.00 

1 


Size... Inches 


41/2 


5 


6 


7 


8 


9 


. 10 


12 ' 


Fig. 62.. -Each 


5.00 


6.00 


8.00 


9.00 


11.00 


12.50 


14.00 


18.00 1 



The largest opening of Reducing Fittings determines the list price. 
Discount 60 and 10 



NOTES ON POWER PLANT DESIGN 



145 



DIMENSIONS OF 
EXTRA HEAVY CAST IRON FLANGED FITTINGS. 

For Steam Working Pressures up to 250 Lbs. 



K— C 



^-A--! 




971 981 



973 



^1 




f--- 

Alk 



991 



1101 



K- A— ^--A— 1 



rn? 







h-B-H 



1021 






1022 






1012 




Size Inches 


1% t 


1% 


2 


21/2 


3 


3y2 


4 


4% 


5 


AA-Face to Face 


8% 1 


9 


10 


11 


12 


13 


14 


15 


16 


A-Center to Face 


41/4 1 


41/2 


5 


51/2 


6 


6V2 


7 


7V2 


8 


B-Centerto Face 


41/4 1 


41/2 


5 


51/2 


6 


6I/2 


7 


772 


8 


C-Center to Face 


_..- 1 





61/2 


7 


7% 


81/2 


9 


91/2 


101/4 


D-Radius 


.__. 1 





51/4 


5% 


6I/4 


evs 


7% 


73/4 


81/2 


E-Center to Face ...^ 


21/2 1 


2% 


3 


31/2 


3y2 


4 


4% 


41/2 


5 


Size Inches 


6 1 


7 


8 


9 


10 


12 


14 


15 


16 


AA-Face to Face 


17 1 


18 


20 


21 


23 


26 


29 


30 


32 


A-Ceriter to Face 


81/2 1 


9 


10 


101/2 


111/2 


13 


141/2 


15 


16 


B-Center to Face .... 


8y2| 


9 


10 


101/2 


111/2 


13 


141/2 


15 


16 


C-Centerto Face 


111/2 1 


12% 


14 


151/4 


I6I/2 


19 


211/2 


22% 


24 


D-Radius 


9% 1 


loys 


12 


13 


141/8 


161/2 


1878 


20 


2iy4 




E-Center to Face 


51/2 1 


6 


6 


6I/2 


7 


8 


8 


81/2 


9 



All Reducing Fittings, IVi inches to 9 inches inclusive, are the same dimensions, Center 
to Face, as straight sizes. For Dimensions of Reducing Fittings 10 inches and larger, 
see lower table. 



Size Inches | 


10 


12 1 


14 


15 1 


16 


18 1 


20 


22 


24 


Size of Outlets | 


6 and 1 8 and 1 9 and 9 and 10 and 1 12 and 1 14 and 1 15 and 1 15 and 
SmallerlSmallerlSmaller Smaller Smaller|Smaller|SmallerlSmaller|SmaIler 


AA-Face to Face of Run | 


18 


21 1 


22 


23 1 


24 


27 1 


30 


30 


30 


A-Center toFace of Run | 


9 


101/2 1 


11 


111/2 1 


12 


13y2| 


15 


15 


15 


B-Cen.to Face of Outlet] 


11 


121/2 1 


131/2 


131/2 1 


15 


I61/2 1 


171/2 


18y2 


191/2 



146 



NOTES ON POWER PLANT DESIGN 



Straight Tee. 



EXTRA HEAVY. 
CAST IRON FLANGED FITTINGS. 

250 Lbs. Working Pressure. 

Reducing Tee. 



FIGURE 1011. 


FIGURE 1012. 1 


Size. 
Inches. 


Faced 
Only. 
Each. 


Faced 

and 
Drilled. 
Each. 


Center 

to 
Face. 
Inches. 


Face 

to 

Face. 

Inches. 


Diam. 

of 
Flanges. 
Inches. 


Size. 
Inches. 


Faced 
Only. 
Each. 


Faced 

and 

Drilled. 

Each. 


Center 

to 
Face. 
Inches. 


Face 

to 

Face. 

Inches. 


2 


7.00 


8.50 


5 


10 


6I/2 


2 


8.00 


9.50 


i 

n 
a, 
<u 

I 

c 
<u 
E 

Q 

1 


2V2 


7.25 


9.00 


5V2 


11 


71/2 


21/2 


8.25 


10.00 


3 


8.25 


10.00 


6 


12 


8I/4 


3 


9.50 


11.25 


31/2 


9.50 


11.25 


6V2 


13 


9 


31/2 


11.00 


12.75 


4 


10.50 


13.50 


7 


14 


10 


4 


12.00 


15.00 


41/2 


13.00 


16.00 


7-/2 


15 


101'2 


4y2 


15.00 


18.00 


5 


14.25 


17.25 


8 


16 


11 


5 


16.25 


19.25 


6 


17.50 


20.50 


8I/2 


17 


121/2 


6 


20.00 


23.00 


7 


23.00 


28.75 


9 


18 


14 


7 


26.50 


32.00 


8 


29.00 


34.75 


10 


20 


15 


8 


33.50 


39.00 


9 


38.00 


44.00 


101/2 


21 


isn 


9 


43.50 


50.00 


10 


46.50 


52.50 


nvo 


23 


i7y2 


10 


53.50 


60.00 


12 


64.00 


73.00 


13 


26 


20 


12 


74.00 


83.00 


14 


84.00 


95.00 


141/2 


29 


221/2 


14 


96.00 


107.00 


15 


105.00 


117.00 


15 


30 


2314 


15 


120.00 


132.00 


16, 


122.00 


135.00 


16 


32 


25 


16 


140.00 


153.00 




1 



Long Radius Elbows. 



Size. 
Inches. 


Faced Only. 
Each. 


Faced and 
Drilled. 
Each. 


Diameter of 
Flanges. 
Inches. 


Radius. 
Inches. 


Center to 
Face. 
Inches. 


2 


9.50 


11.50 


6y2 


5% 


6y2 


2V2 


10.00 


12.50 


71/2 


5% 


7 


3 


11.50 


14.00 


8% 


6% 


7% 


3V2 


13.00 


15.50 


9 


6Vs 


8y2 


4 


14.50 


18.50 


10 


7% 


9 


41/2 


18.00 


22.00 


101/2 


7% 


9% 


5 


19.50 


23.50 


11 


8y2 


10% 


6 


24.00 


28.00 


121/2 


9% 


im 


7 


32.00 


39.50 


14 


lOVs 1 12% 


8 


40.00 


47.50 


15 


12 


14 


9 


52.00 


60.00 


i6y4 


13 


i5y4 


10 


64.00 


72.00 


17% 


141/8 


i6y2 


12 


88.00 


100.00 


20 


i6y2 


19 


14 


116.00 


130.00 


22y2 


18% 


211/2 


15 


144.00 


160.00 


23y3 


20 


22y4 


16 


168.00 


186.00 


25 1 2iy4 


24 





90° Elbow. 






45° Elbow. 






FIGURE 971. 


FIGURE 972. 




Size. 
Inches. 


Faced 
Only. 

Each. 


Faced and 
Drilled. 
Each. 


Center to 
Face. 
Inches. 


Size. 
Inches. 


Faced 
Only. 
Each. 


Faced and 
Drilled. 
Each. 


Center to 
Face. 
Inches. 


Diam. of 
Flanges. 
Inches. 


2 


4.75 


5.75 


5 


2 


5.25 


6.25 


3 


6I/2 


21/2 


5.00 


6.25 


511. 


21/2 


5.50 


6.75 


3% 


71/2 


3 


5.75 


7.00 


6 


3 


6.25 


7.50 


31/2 


81/4 


31 '2 


6.50 


7.75 


61/2 


SVa 


7.25 


8.50 


4 


9 


4 


7.25 


9.25 


7 


4 


8.00 


10.00 


4y2 


10 


41'2 


9.00 


11.00 


7y2 


41/2 


10.00 


12.00 


41/2 


101/2 


5 


9.75 


11.75 


8 


5 


10.75 


12.75 


5 


11 


6 


12.00 


14.00 


81/2 


6 


13.00 


15.00 


51/2 


121/2 


7 


16.00 


19.75 


9 


7 


16.00 


19.75 


6 


14 


8 


20.00 


23.75 


10 


8 


20.00 


23.75 


6 


15 


9 


26.00 


30.00 


101/2 


9 


26.00 


30.00 


61/2 


161,4 


10 


32.00 


36.00 


iiy2 


10 


32.00 


36.00 


7 


171/3 


12 


44.00 


50.00 


13 


12 


44.00 


50.00 1 8 


20 


14 


58.00 


65.00 


i4y2 


14 


58.00 


65.00 8 


221/2 


15 


72.00 


80.00 


15 


15 


72.00 


80.00 1 8y2 


23y3 


16 


84.00 


93.00 


16 


16 


84.00 


93.00 1 9 


25 







Straight Cross. 






Reducing Cross. 






FIGURE 1021. 


FIGURE 1022. | 


Size; 
Inches. 


Faced 
Only. 
Each. 


Faced 

and 

Drilled. 

Each. 


Center 

to 
Face. 
Inches. 


Face 

to 

Face. 

Inches. 


Diam. 

of 
Flanges. 
Inches. 


Size. 
Inches. 


Faced 
Only. 
Each. 


Faced 

and 

Drilled. 

Each. 


Center 

to 
Face. 
Inches. 


Face 

to 
Face. 
Inches. 


2 


9.50 


11.50 


5 


10 


6y2 


2 


11.00 


13.00 


S! 

c 

c 
E 

1 


2y2 


10.00 


12.50 


5y2 


11 


7% 


2y2 


11.50 


14.00 


3 


11.50 


14.00 


6 


12 


8% 


3 


13.25 


15.75 


3y3 


13.00 


15.50 


6y2 


13 


9 


31/2 


15.00 


17.50 


4 


14.50 


18.50 


7 


14 


10 


4 


16.75 


20.75 


4y2 


18.00 


22.00 


71/2 


15 


ioy2 


■41/2 


20.75 


25.00 


5 


19.50 


23.50 


8 


16 


11 


5 


22.50 


26.50 


6 


24.00 


28.00 


81/2 


17 


121/2 


6 


27.50 


31.50 


7 


32.00 


39.50 


9 


18 


14 


7 


37.00 


45.00 


8 


40.00 


47.50 


10 


20 


15 


8 


46.00 


53.50 


9 


52.00 


60.00 


101/2 


21 


16U 


9 


60.00 


68.00 


10 


64.00 


72.00 


111/2 


23 


17% 


10 


74.00 


82.00 


12 


88.00 


100.00 


13 


26 


20 


12 


100.00 


112.00 


14 


116.00 


130.00 


i4y2 


29 


22y2 


14 


132.00 


146.00 


15 


144.00 


160.00 


15 


30 


23y2 


15 


165.00 


180.00 


16 


168.00 


186.00 


16 


32 


25 


16 


193.00 


210.00 




1 



Discount on all Flanged Fittings 60 per cent. 



EXTRA HEAVY. 

CAST IRON FLANGED FITTINGS. 

250 Lbs. Working Pressure. 



Reducing Taper Elbows. 



Size. 
Inches. 


FIGURE 981. 


Diameter of 
Flanges. 
Inches. 


Center 

to 

Face. 

Inches. 


Size. 
Inches. 


FIGURE 981. 


Dicimeter of 
Flanges. 
Inches. 


Center 

to 

Face. 

Inches. 


Faced 
Each. 


Faced 

and 

Drilled. 

Each. 


Faced 
Each. 


Faced 

and 

Drilled. 

Each. 


2 KlVi 


9.50 


11.50 


6y2X 5 


5 


7x 5 


32.00 


39.50 


14 xll 


9 


2 X m 


9.50 


11.50 


6Hx 6 


5 


7x 6 


32.00 


39.50 


14 x 12y2 


9 


2y2xiy2 


10.00 


12.50 


7y2X 6 


51-'2 


8x 4 


40.00 


47.50 


15 xlO 


10 


2^2x2 


10.00 


12.50 


7y2x 6y2 


5y2 


8x 5 


40.00 


47.50 


15 xll 


10 


3 XIV2 


11.50 


14.00 


8y4x 6 


6 


8x 6 


40.00 


47.50 


15 X 12y2 


10 


3 x2 


11.50 


14.00 


81,4 X 6y2 


6 


8x r 


40.00 


47.50 


15 xl4 


10 


3 X 2y2 


11.50 


14.00 


8y4x 7y2 


6 


10 X 5 


64.00 


72.00 


i7y2 X 11 


iiyo 


3y2x2 


13.00 


15.50 


9 X 672 


6y2 


10 X 6 


64.00 


72.00 


i7y2 X i2y2 


iiy2 


3% X 21/2 


13.00 


15.50 


9 X 7y2 


6y2 


lOx 8 


64.00 


72.00 


i7y2 X 15 


iiy2- 


3^2x3 


13.00 


15.50 


9 X 8% 


6y2 


12 X 7 


88.00 


100.00 


20 xl4 


13 


4 x2 


14.50 


18.50 


10 X 6y2 


7 


12 X 8 


88.00 


100.00 


20 xl5 


13 


4 x2y2 


14.50 


18.50 


10 X 7y2 


7 


12 X 9 


88.00 


100.00 


20 X I614 


13 


4 x3 


14.50 


18.50 


10 X 8V4 


7 


12x10 


88.00 


100.00 


20 X 17y2 


13 


4 x3y2 


14.50 


18.50 


10 X 9 


7 


14 X 6 


116.00 


130.00 


22y2 X i2y2 


i4y2 


5 x2y2 


19.50 


23.50 


11 X 7y2 


8 


14x10 


116.00 


130.00 


22y2 X i7y2 


i4y2 


5 x3 


19.50 


23.50 


11 X 8% 


8 


14x12 


116.00 


130.00 


22y2 X 20 


i4y2 


5 x4 


19.50 


23.50 


11 xlO 


8 


15x 6 


144.00 


160.00 


23y2 X i2y2 


15 


6 x3 


24.00 


28.00 


i2y2x 8y4 


8y2 


15x10 


144.00 


.160.00 


23y2 X i7y2 


15 


6 »3y2 


24.00 


28.00 


i2y2x 9 


8y2 


15x12 


144.00 


160.00 


23y2x20 


15 


6 x4 


24.00 


28.00 


i2y2 xio 


8y2 


16x 8 


168.00 


186.00 


25 xl5 


16 


6 X 4y2 


24.00 


28.00 


i2i^xioy2 


8y2 


16x10 


168.00 


186.00 


25 X 17y2 


16 


6 x5 


24.00 


28.00 


i2y2 X 11 


8y^ 


16x12 


168.00 


186.00 


25 x20 


16 


■7 x4 


32.00 


39.50 


14 xlO 


9 


16x14 


168.00 


186.00 


25 X 22y2 


16 



Pipe Size 

and 0. D. of 

Flange. 

Inches. 


Screwed Flange. 


Blank Flange. 


Price 
of Bolts 
per Set 
for One 
Joint. 


Threading 

Pipe, Making 

On and 

Refacing, 

Not Including 

Flange. 

Net Each. 


Faced 
Only. 
Each. 


Faced 

and 

Drilled. 

Each. 


Faced 
Only. 
Each. 


Faced 

and 

Drilled. 

Each. 


1 X 4y2 


1.00 


1.25 








.20 


.60 


iy4x 5 


1.05 


1.35 








.20 


.60 


iy2x 6 


1.10 


1.40 








.25 


.65 


2 x 6y2 


1.20 


1.50 


1.40 


1.70 


.25 


.70 


2y2x 7y2 


1.40 


2.00 


1.60 


2.20 


.40 


.75 


3 X 8y4 


1.60 


2.25 


1.85 


2.50 


.55 


.85 


3y2x 9 


- 1.80 


2.50 


2.10 


2.80 


.55 


.90 


4 xlO 


2.15 


3.00 


2.50 


3.35 


.80 


.95 


4y2 X ioy2 


2.50 


3.35 


2.91) 1 3.75 


-.80 


1.00 


5 xll 


2.80 


3.65 


3.25 


4.10 


.80 


1.10 


6 X 12y2 


3.20 


4.00 


3.70 


4.50 


1.15 


1.25 


7 xl4 


4.35 


5.75 


5.00 


6.40 


1.80 


1.35 


8 xl5 


5.00 


6.50 


«, 5.75 


7.25 


1.80 


1.55 


9 X 161/4 


6.75 


8.25 


7.75 


9.25 


1.80 


1.80 


10 X 17y2 


7.75 


9.25 


9.00 


10.60 


2.60 


2.00 


12 x20 


10.50 


12.50 


14.00 


16.00 


2.75 


2.75 


14 X 22y2 


13.75 


16.00 


17.50 


19.75 


3.60 


3.50 


15 X 23y2 


18.00 


21.00 


22.50 


25.50 


4.75 


3.75 


16 x25 


22.50 


26.00 


28.00 


31.50 


4.75 


4.75 


18 x27 


27.50 


31.00 


33.00 


36.50 


5.60 


7.00 


20 X 29y2 


30.00 


34.00 


36.00 


40.00 


8.30 


8.25 


22 x3iy2 


33.75 


39.00 


41.00 


46.00 


10.00 


9.50 


24 x34% 


41.00 


46.00 


50.00 


55.00 


10.00 


11.00 



Discount on all Flanged Fittings 60 per cent. 



EXTRA HEAVY. 
CAST IRON SCREWED FITTINGS. 

250 Lbs. Working Pressure. 
FLANGE UNIONS. 



size. 
Inches. 


Diameter of 
Flanges. 


Diameter of 
Bolt Circle. 


Number of 
Bolts. 


Price. 
Each. 


^4 


3 


2 


4 


.60 


% 


3% 


2% 


4 


.70 


1 


3% 


2% 


4 


.80 


1% 


4% 


3y8 


4 


1.00 


IV2 


4% 


3y2 


4 


1.15 


2 


sy, 


4V8 


5 


1.50 


2y2 


m 


4% 


5 


1.90 


3 


eys 


5% 


6 


2.25 


3y2 


7y2 


6 


6 


2.70 


4 


8 


6y2 


7 


3.15 


4y2 


8% 


Tys 


8 


4.00 


5 


9y2 


7% 


8 


4.75 


" 


lOVs 


9y8 


9 


6.00 


7 


12 


10% 


10 


8.25 


8 


isy* 


11% 


10 


10.50 



LONG SWEEP FITTINGS. 
CAST IRON. 

For Steam Working Pressures to 125 Lbs. 
For Water Working Pressures to 175 Lbs. 



DOUBLE SWEEP 
TEES. 



-A— i 



291 



^ 



Size Inches 


1 iy4 iy2 2 2y2 3 3y2 4 


Fig. 291, Tees Eacii 


.64 .80 1.10 1.60 2.40 4.50 6.50 7.00 


Reducing Tees Each 


.96 1.20 1.65 2.40 3.60 6.75 9.75 10.50 


A-Center to Face Inches 


2% 2% 3 3% 4% 5y2 53/4 eVs 


Size Inches 


4y2 5 6 7 8 9 10 12 


Fig. 291, Tees ..Each 


11.00 13.00 17.50 26.00 34.00 51.00 60.00 80.00 


Reducing T|es Each 1 16.50 19.50 26.25 39.00 51.00 | 76.50 1 90.00 1 120.00 


A-CentertoFace_ Inches | 6y4 7 7y2 SVs 9iV2 | 10% | 1^1 12% 



EXTRA LONG SWEEP 
ELBOWS. 




'SSZ 



Size .--. 


, . Inches 


1 


m 


iy2 2 2y2 3 


3% 4 


Fig. 292, Elbows...,.-.. 


...Each 


.50 


.70 


.90 1.20 2.00 3.00 


4.00 5.00 


B-Center to Face . . : 


..Inches 


3yi« 


3% 


4 sya eys 7y4 


8y4 10% 


C-Radius 


. . Inches 


2% 


2% 


3% 4% 5y4 5% 


6% 9y8 


Size 


..Inches 


4y2 


5 


6 7 8 9 


10 12 


Fig. 292, Elbows 


...Each 


7.00 


9.00 


\Zm 20.00 28.00 34.00 


40.00 60.00 


B-Center to Face 


..Inches 


loys 


11% 


13 14y2 I8V4 21% 


24% 31 


CRadlus 


..Inches 


9% 


9% 


11% 12% 16% 1 198/4 


22% 28% 



Straight sizes furnished galvanized at double the above lists, and regular discounts. 



Discount 60 and 10 



NOTES ON POWER PLANT DESIGN 



149 




DIMENSIONS OF 

MEDIUM PRESSURE 
GATE VALVES. 



k- A-H 
Fig. 1521. Screwed. 




Fig. 1522. Flanged. 



Size 


Ins. 


2 


21/2 


3 


31/2 


4 


4y2 


5 


6 


A-Fig. 1521 


Ins. 


51/2 


6 


71/4 


71/2 


7% 


81,4 


8I/2 


8% 


B-Fig. 1522 


Ins. 


71/2 


8 


91/2 


10 


ioy2 


11 


111/2 


12 


C-Center to Top of Wheel 


Ins. 


111/2 


121/2 


15 


16% 


19 


20 


22 


251/4 


D-Center to Top of Spindle, Open, 


Ins. 


14 


151/2 


i8y2 


2OV2 


23% 


25 


28 


32 


E-Diameter of Wheel 


Ins. 


61/2 


eva 


71/2 


7y2 


9 


9 


10 


12 


F-Diameter of Flange 


Ins. 


61/2 


71/2 


8Vi 


9 


10 


101/2 


11 


121/2 


G-Thickness of Flange 


Ins. 


% 


1 


1V8 


13/16 


ly* 


1%6 


1% 


1%6 


Size 


Ins. 


7 


8 


9 


10 


12 









B-Fig. 1522 


Ins. 


121/2 


131/2 


14 


15 


16 





--,- 





C-Center to Top of Wheel 


Ins. 


28 


32 


34 


39 


44 











D-Center to Top of Spindle, Open_Ins. 


36 


41 


44 


5a 


57 








_-_- 


E-Diameter of Wheel 


Ins. 


12 


14 


14 


16 


18 





-,-- 





F-Diameter of Flange 


Ins. 


14 


15 


16y4 


i7y2 


20 











G-Thickness of Flange 


Ins. 


11/2 


1% 


1% 


1% 


2 











Size Inches 


2 


2y2 


3 


31/2 


4 


41/2 


5 


6 


Fig. 1521 _.. Each 


23.00 


25.00 


29.00 


35.00 


40.00 


50.00 


54.00 


65.00 


Fig. 1522 Each 


25.50 


27.50 


32.00 


38.00 


45.00 


55.00 


59.00 


72.00 


Drilling Each 


.75 


.75 


.75 


1.00 


1.25 


1.50 


1.50 


1.75 


Size Inches 


7 


*8 


9 


10 


12 











Fig. 1522 Each 


97.00 


117.00 


152.00 


178.00 


225.00 











Drilling Each 


2.25 


2.25 


2.50 


2.50 


3.50 


1 .... 









This valve is suitable for 
The discount is 50 and 5 



pressure up to 175 lbs. 
per cent. 



ISO 



NOTES ON POWER PLANT DESIGN 




DIMENSIONS OF 

EXTRA HEAVY 

OUTSIDE SCREW 
AND 
YOKE GATE VALVES. L 



Fig. 1581. 




Size 


---Inches 


21/2 


3 


31/2 


4 


41/2 


5 


6 


A-Fig. 1581 


---Inches 


81/8 


91/2 


11% 


12% 


14 


15% 


I61/4 


B-Fig.l582 


---Inches 


9V2 


llVs 


11% 


12 


131/i 


15 


15% 


C -Center to Top . 


_ _ _ Inches 


13V2 


isys 


171/8 


18% 


23% 


23% 


25% 


D Center to Top of Stem, Open .. 


Inches 


ley* 


18% 


21 


23% 


29y4 


29y4 


31% 


E-Diameter of Wheel 


Inches 


8 


10 


10 


11 


11 


12 


13 


F-Diameter of Flange 


---Inches 


71/2 


8% 


9 


10 


101/2 


11 


121/2 


G-Thickness of Flange 


-.-Inches 


1 


11/8 


13/10 


1% 


P/ie 


1% 


F/io 


Size 


--.Inches 


7 


8 


9 


10 


12 





— .- 


B.Fig.l582.... 


...Inches 


16% 


I61/2 


17 


18 


19% 








C-Center to Top 


---Inches 


29% 


321/2 


36% 


39% 


451/4 








D-Center to Top of Spindle, Open 


.--Inches 


371/2 


41% 


461/3 


501/2 


58 '/2 








E-Diameter of Wheel 


. . . Inches 


15 


15 


16 


16 


18 







F-Diameter of Flange 


...Inches 


14 


15 


16% 


171/2 


20 








G-Thickness of Flange 


_. -Inches 


11/2 


1% 


1% 


1% 


2 








Size Inches 


21/2 


3 


31/2 


4 


4% 


5 


6 


Fig. 1581 Each 


41.00 


54.00 


67.00 


72.00 


92.00 


100.00 


115.00 


Fig. 1582 Each 


43.50 


57.00 


70.00 


77.00 


97.00 


105.00 


122.00 


Drilling Each 


.75 


.75 


1.00 


1.25 


1.50 


1.50 


1.75 


Size . Inches 


7 


*8 


9 


10 


12 








Fig. 1582 Each 


147.00 


187.00 


257.00 


283.00 


390.00 





.... 


Drilling ..Each 


2.25 


2.25 


2.50 


2.50 


3.50 








Discount 60 per cent. 



NOTES ON POWER PLANT DESIGN 



151 



DIMENSIONS OF 

EXTRA HEAVY GATE VALVES. 

WITH BY-PASS. 




Size 




.Inches 


6 


7 


8 


9 


• 10 


Face to Face, Flanged 




.Inches 


15% 


161/4 


I61/2 


17 


18 


C-Center to Top 




-Inches 


25% 


29% 


321/2 


361/2 


39% 


E-Diameter of Wheel 




. Inches 


13 


15 


15 


16 


16 


D-Center to Top of Spindle 


, open _ _ 


.Inches 


32 


38 


41 


46, 


50 


H-Center to Outside of By-Pass. .. 


.Inches 


14 


15 


16 


16^2 


171/2 


Diameter of Flange 




.Inches 


12V2 


14 


15 


16M 


171/2 


Thickness of Flange 




-Inches 


F/lG 


11/2 


1% 


1% 


1% 


Size of By-Pass 




.Inches 


IVa 


11/j 


11/2 


11/2 


11/2 


Size 




.Inches 


12 


14 


15 


16 





Face to Face, Flanged _. 




.Inches 


19% 


211/2 


221/2 ! 


24 









C-Center to Top 




.Inches 


45y4 


501/2 


521/2 1 


58 





E-Diameter of Wheel 




.Inches 


18 


22 


22 1 


24 





D-Center to Top of Spindle 


, open.. 


.Inches 


581/2 


66 


69 1 


751/2 1 





H-Center to Outside of By- Pass.. . 


.Inches | 


20 1 


21 


2iy2 1 


27 1 


- 


Diameter of Flange 




.Inches | 


20 1 


221/2 1 


23V2 1 


25 1 





Thickness of Flange 




.Inches | 


2 1 


21/8 1 


2% 6 1 


21/4 1 





Size of By-Pass 




.Inches | 


2 1 


2 1 


2 _.J 


.3 1 




Size 


Inches 


*6 


7 


8 


9 


10 


12 ^ 


Fig. 1601 


..Each 


170.00 


195.00 


240.00 


310.00 


335.00 


455 00 


Drilling 


..Each 


1.75 


2.25 


2.25 


2.50 


2.50 


3.50 


Size 


Inches 


14 


15 


16 











Fig. 1601 


..Each 


580.00 


680.00 


825.00 











Drilling 


..Each 


4.00 


4.00 


5.00 


-- 





.... 



* 6-inch Valves have Bronze Spindles. 
Larger sizes. Steel Spindles, Nickel Plated. 
Discount 60 per cent. 



152 



NOTES ON POWER PLANT DESIGN 



DIMENSIONS OF 

EXTRA HEAVY 

IRON BODY GLOBE AND ANGLE VALVES. 




1981 



.•^-F-- -> 




1982 



Size Inches 



21/2 



3y2 



4 



4% 



A-End to End Inches 



IOV2 IIV2 



12% 13 14 14% 161/2 



"I -Center to End ._ 



-Inches 



5% 



5% 



63/8 6I/2 



1% 81/i 



B-Face to Face Inches 



111/2 



121/2 



131/2 



14 



15 15% 171/2 



^-Center to Face Inches 



5% 



6% 



6% 



71/2 VA 8% 



C-Center to Top, Closed Inches 



13 



14 



15% 16% 171/2 



18 



20 



D-Center to Top, Open Inches 



141/2 



15% 



17% 



19 



20 



20% 231/2 



E-Diameter ofWheel Inches 



12 



12 



14 



16 



F-Diameter of Flange Inches 



71/2 



81/^ 



10 101/2 



11 



I2V2 



G-Thickness of Flange Inches 



1%. 



11/^ 



15/lC 



1% 



F/k 



Size -• Inches 



10 



12 



B-Face to Face Inches 



191/4 



21 



241/2 28 



§ -Center to Face Inches 



9% 



101/2 



121/4 14 



C-Center to Top, Closed Inches 



211/2 



25 



28 



32 



D-Center to Top, Open Inches 25i/4 



29 



33 



38 



E-Diameter of Wheel Inches 16 



20 



24 



30 



F-Diameter of Flange Inches 14 



15 



171/2 20 



G-Thickness of Flange Inches 



11/2 



1% 



V/s 



Size Inches 



21/2 



3y2 



Globe or Angle Valves, Screwed Ends Each 



33.00 



37.00 



42.00 



46.00 



Globe or Angle Valves, Flanged Ends Each 



35.00 



40.00 



45.00 



50.00 



Fig. 1981, Drilling Each 



.75 



.75 



1.00 



1.25 



Fig. 1982, Dialling Each 



1.25 



1.25 



1.50 



1.75 



Size _' Inches 



41/2 



Globe or Angle Valves, Screwed Ends Each 



56.00 



61.00 



75.00 



Globe or Angle Valves, Flanged Ends Each 



60.00 



65.00 



80.00 



Fig. 1981, Drilling Each 



1.50 



1.50 



1.75 



Fig. 1982, Drilling Each 



2.00 



2.00 



2.50 



Size Inches 



10 



12 



Globe or Angle Valves, Flanged Ends Each 



100.00 



120.00 



200.00 



300.00 



Fig. 1981, Drilling Each 



2.25 



2.25 



2.50 



3.5o 



Fig. 1982, Drilling Each 



3.00 



3.00 



3.50 



5.00 



Discount 60 per cent. 



NOTES ON POWER PLANT DESIGN 
PRILLING TEMPLATES 

FOR 
FLANGED VALVES, FLANGED FITTINGS AND FLANGES. 

250 Lbs. Working Pressure. 



153 



size. 
Inches. 


Diameter of 
Flanaes. 


Thickness of 
Flanges. 


Bolt 
Circle. 


Number of 
Bolts. 


Size of 
Bolts. 


Length of 
Bolts. 


1 


4% 


^%6 


m 


4 


% 


2 


IVi 


5 


% 


3% 


4 


% 


2y4 


1% 


6 


i?ie 


4% 


'4 


% 


2% 


2 


m 


% 


5 


4 


% 


2% 


2V2 


m 


1 


5% 


4 


% 


3 


3 


&Vi 


1% 


6% 


8 


% 


3 


3% 


9 


l%e 


n'i 


8 


% 


SVi 


4 


10 


IH 


7% 


8 


% 


3% 


4H 


WVi 


1%6 


8% 


8 


% 


3% 


5 


- 11 


1% 


9% 


8 


% 


3% 


6 


12^! 


I'Ae 


10% 


12 


% 


3% 


7 


14 


1% 


11% 


12 


Vs 


4 


6 


15 


1% 


13 


12 


% 


m 


9 


16% 


1%, 


14 


12 


1 


4% 


10 


17% 


1% 


15H 


16 


1 


4% 


12 


20 


2 


17% 


16 


1 


5 


14 


22% 


2% 


20 


20 


1 


5% 


15 


23% 


' 2?46 


21 


20 


1% 


5% 


16 


25 


2% 


22% 


20 


1% 


5% 


18 


27 


2% 


24% 


24 


1% 


6 


20 


29% 


2% 


26% 


24 


IH 


6% 


22 


31% 


2% 


28y4 


28 


ly* 


6% 


24 


34W 


2% 


3Wi 


28 


1% 


7 





From Wall to Center of Pipe, Adjustable ^ fnthes 



Horizontal Center between Wall Bolts Inches 



Vertical Center between Wall Bolts , Incl,g3 



From Wall to End of Bracket. _.^ j^ 

Price, including Wall Bolts 



-Each 



15 to 19 



18% 



27 



28.00 




Discount on Cast Iron Rolls, Chains and Wall Brackets 373^ per cent. 



154 



NOTES ON POWER PLANT DESIGN 



SEAMLESS DRAWN BRASS PIPE. 



STANDARD IRON PIPE SIZES. 



Iron 
Pipe 
Sizes. 


Actual 
Outside 
Diameter. 


Actual 

Inside 

Diameter. 


Approximate 

Wt. per Foot 

Pounds.* 


Iron 
Pipe 
Sizes. 


Actual 
Outside 
Diameter. 


Actual 

Inside 

Diameter. 


Approximate 

Wt per Foot 

Pounds.* 


Vs 


. .405 


.281 


.25 


2'i 


2.875 


2.5 


5.75 


H 


.540 


.375 


.43 


3 


3.500 


3.062 


8.30 


% 


.675 


.494 


.62 


3>/2 


4.000 


3.5 


10.90 


1/2 


.840 


.625 


.90 


4 


4.500 


4. 


12.7C 


% 


1.050 


.822 


1.25 


414 


5.000 


4.5 


13.90 


1 


1.315 


1.062 


1.70 


5 


5.563 


5.062 


15.75 


1% 


1.660 


1.368 


2.50 


6 


6.625 


6.125 


18.31 


V/2 


1.900 


1.6 


3.00 


7 


7.625 


7.082 


23.73 


2 . 


2.375 


2.062 


4.00 


8 


8.620 


7.980 


29.88 


EXTRA HEAVY IRON PIPE SIZES. 


Iron 
Pipe 
Sizes. 


Actual 

Outside 

Diameter. 


Actual 

Inside 

Diameter. 


-Approximate 

Wt. per Foot 

Pounds.* 


Iron 
Pipe 
Sizes. 


Actual 
Outside 
Diameter. 


Ac^Jal 

Inside 

Diameter. 


.Approximate 

VVL per Foot 

Pounds.* 


Vs 


.405 ■ 


.205 


.370 


2 


2.375 


1.933 


5.460 


M 


.540 


.294 


.625 


2'b 


2.875 


2.315 


8.300 


% 


.675 


.421 


.830 


3 


3.500 


2.892 


11.200 


V2 


.840 


.542 


1.200 


3>,i 


4.00 


3.358 


13.700 


% 


1.050 


.736 


1.660 


4 


4.50 


3.818 


16.500 


1 


1.315 


.951 


2.360 


5 


5.563 


4.813 


22.800 


l^i 


1.660 


1.272 


3.300 


6 


6.625 


5.750 


32.00 


I'.fe 


1.900 


1.494 


4.250 





* Some variation must be expected in these weights. 

Stock lengths of Is inch to 2 inches Standard Weight Pipe average 16 feet in length ; 
2Vi inches to 4 inches, 14 feet to 16 feet ; 5 inches to 6 inches, 10 feet to 12 feet 
Stocl< lengths of Extra Heavy Pipe run somewhat shorter than Standard Weight 



BRASS FITTINGS. 

EXTRA HEAVY— IRON PIPE SIZE. 

CAST IRON PJ^TTERN. 

For 250 Lbs. Steam Working Pressure. 

TEES, CROSSES, AND Y BENDS. 



BRASS FLANGED FITTINGS 
STANDARD WEIGHT. 

For 125 Lbs. 



Size Inches 1 I4 



1 1 lU ! lU- 



2ij 



Size Inches 



3K. I 4 



41^ 



Elbows, 90°. Faced Each 25.00 33.75 43.75 58.75 68.00, 78.00 93.00123.00 



90O, Faced and Drilled. ...Each 26.00 35.00 45.00 60.00 70.00 80.00 95.001125.00 



Elbows, 450, Faced Each 27.50 37.25 47.75, 63.75,73.00 83.00 98.00,133.00 



45", Faced and Drilled Each 28.50 38.50 49.00 65.001 75.00 85.00 100.00 135.00 



Tees. Faced __Each 37.50 50.75 65.75 88.25 102.00 117.00137.00187.00 



Faced and Drilled Each 39.00 52.50 67.50 90.00 105.00 120.00 140.00 190.00 



Tees Each I 35 1 .40 .65 1.00 1.35 i 2.00 3.00 4.50 1 7.50 11.00 16.50 20.00 



Crosses, Faced Each 50.00 67.50 87.50 117.50 136.00156.00186.00 246.00 



Tecs, Reducing 



-Each 



.46 ' .75 1.15' 1.55 2.30 3.45 ' 5.20 ' 8.60 12.65 .-_ ! 22.00 



Faced and Drilled 



.Each 52.00,70.00 90.00 120.00 140.00 160.00 190.00 250.00 



Crosses. 



. Each 



.90 1.301 1.80 2.75 4.00 ' 5.25 ' 9.00 14.00 21.00: 27.00 



Companion Flanges, Faced ...Each 10.75 12.5015.50 19.25 24.25 26.75 29.00 36.50 



Crosses. Red Each 



.. 11.04 1.50 2.10 I 3.15 i 4.60 ' 6.00 10.35 16.00 24.00 30.00 



Faced and Drilled Each 11.0013.0016.00 20.00 25.00 27.50 30.00i 37.50 



Y Bends Each 



1.30 1.35 2.25 I 2.90 ' 4.25 '. 6.50 i 9.60!l3.25 22.50; 30.00 



Finished Fittings at double above lists. 



ELBOWS. 



Dimensions same as Standard Weight Cast Iron Fittings. 
Reducing sizes to order at special prices. 

EXTRA HEAVY. 

For 250 Lbs. Steam Working Pressure. 



Size Inches | ¥4 1 % | V-i \ ^a \ 1 | Ui | IV2 1 2 i 21/2 ^ 3 ! 3V2 i 4 


Size 


-Inches 1 2 ' 2'. ' 3 ! S'i. ! 4 1 4^<2 1 5 I 6 


Elbows..-. Each | .25 1 .28 .36 [ .70 i 1.00 ! 1.50 ! 2.00 I 3.00 ' 5.50 i 8.5012.50, 16.00 


Elbows. 90", Faced 


.-Each 125.00 33.75 43.75 58.75 68.00 78.001 93.00123.00 


Elbows, Red Each i .. | .32 i .42 1 .80 i 1.15 i 1.72 i 2.30 3.45 i 6.30 1 9.75 14.50 18.50 


90", Faced and Drilled ._ 


-.Each 26.00 35.00 45.00 60.00 70.00! 80.00^ 96.00i 125.00 


Elbows, 45", Faced 


--Each 27.50 37.25 47.75 63.75 73.00' 83.001 98.00133.00 


Elbows, R. and L. Each , .. 1 .32 '' .42 i .80 ■ 1.15 1 1.72 2.30 3.45 i 6.30 ! 9.75; ... ! ... 


45", Faced and Drilled .. 


Each 28.50 38.50 49.00 65.00 75.00: 85.00100.00135.00 


Elbows, 45° Each ! .35 : .40 .43 1 .84 1 1.20 1 1.80 , 2.40 i 3.60 ■ 6.60 j 10.20 15.50i 20.00 


Tees, Faced 


-Each 37.50 50.75 65.75 88.25102.00117.00137.00187.00 


Finished Fittings at double above lists. 


Faced and Drilled 


..Each 39.00 52.50 67.50 90.00105.00120.00140.00190.00 


Crosses, Faced 


Each 50.00 67.50 87.50 117.50 136.00 156.00 186.00 246.00 




Faced and Drilled 


Each 52.00 70.00 90.00! 120.00 140.00 160.00 190.00 250.00 




Companion Flanges, Faced. 


.-Each 1IO.75 12.50 15.501 19.25 24.25 26.75 29.00, 36.50 




Facedand Drilled 


Each 11.0013.0016.001 20.00 25.001 27.501 30.001 37.50 



Dimensions same as Extra Heavy Cast Iron Fittings. 
Reducing sizes to order at special prices, 



Discount on all brass fittings flanged or screwed, 65 per cent. 



NOTES ON POWER PLANT DESIGN 



155 



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nil III nil 1 II II 1 11 








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In figuring the cost of a bent pipe, add to the net cost of the pipe and flanger the following for each bend of 
90° or less 

For pipe size 6" 7" 8" 9" 10" 12" 

add per bend $8 $9 $12 $13 $16 $26 



156 NOTES ON POWER PLANT DESIGN 

CAST IRON PIPE 

Cast iron pipe may be used to convey cooling water to the power house. This pipe comes 
in lengths of about twelve feet and has a bell on one end and a spigot on the other. The joint be- 
tween the bell and spigot is made by pouring in melted lead and then calking with a blunt chisel. 

A table giving the weights of cast iron pipe is convenient in figuring costs which are taken 
at a certain rate per ton, the price depending upon the price of pig iron. The price is between 

and 125 a ton. 

DIMENSIONS OF CAST IRON PIPE 

Standard adopted by American Water Works Association. 

The weight per length refers to length of 12 feet and includes allowance for bell and spigot. 





Class A, 100 ft. 


Head 


Class B, 200 ft 


.Head 


Class C, 300 ft. 


Head 


Nominal 


Thick- 


Weight Lbs. 


Thick- 


Weight Lbs. 


Thick- 


Weight Lbs. 


inside 


ness 


Ft. 


Length 


ness 


Ft. 


Length 


ness 


Ft. 


Length 


dia. 


In. 






In. 






In. 






8 


.46 


42.9 


515 


.51 


47.5 


570 


;56 


52.1 


625 


10 


.50 


57.1 


685 


.57 


63.8 


765 


.62 


70.8 


850 


12 


.54 


72.5 


870 


.62 


82.1 


985 


.68 


91.7 


1100 


14 


.57 


89.6 


1075 


.66 


102.5 


1230 


.74 


116.7 


1400 


16 


.60 


108.3 


1300 


.70 


125.0 


1500 


.80 


143.8 


1725 


18 


.64 


129.2 


1550 


.75 


150.0 


1800 


.87 


175.0 


2100 


20 


.67 


150.0 


1800 


.80 


175.0 


2100 


.92 


208.2 


2500 


24 


.76 


204.2 


2450 


.89 


233.3 


2800 


1.04 


279.2 


3350 


30 


.88 


192.7 


3500 


1.03 


333.3 


4000 


1.20 


400.0 


4800 


36 


.99 


391.7 


4700 


1.15 


454.2 


5450 


1.36 


545.8 


6550 



NOTES ON POWER PLANT DESIGN 



157 



PIPE COVERING 



The heat radiated from a bare pipe is about 3 B. T. U. per hour per square foot of pipe sur- 
face per degree difference in temperature between the steam inside the pipe and the air in the room. 

The saving made by coverings of different thickness is shown by the figures below which apply 
to a 5" pipe: 



B. T. U. loss per hour per square foot 

of surface of 5" pipe per degree 

diff. in temperature .... 



Bare Pipe 

No 
Covering 



3.00 



Covering Covering Covering Covering 



1/" 

72 

Thick 



.67 



1' 
Thick 



.43 



Thick 



.37 



Thick 



.33 



The B. T. U. loss per square foot of pipe surface per hour per degree difference in temperature 
gradually increases for the covered pipes as the diameter of the pipe decreases, the values for a 
2" pipe being about 20 per cent greater than the values given above. For sizes over 5" diameter 
the values gradually decrease until at 10" diameter, the figures are 10 per cent lower than those 
given. 

The efficiency of a covering, or the percentage of heat saved, varies slightly with different cov- 
erings of the same thickness, in general, however, a covering 3" thick may be assumed to have 
an efficiency of 88 per cent and one, IM" thick, 85 per cent. 

The saving per year due to covering an 8" header 200 feet long supplied with steam at 170 
lbs. absolute superheated 100° may be figured thus. 

For high pressure steam, 100 to 150 lbs., the Double Layer Double Standard Thickness sectional 
covering should be used. This covering should be applied by the broken joint method, each set 
of sections being thoroughly wired in place. Outside of the sections 3^" of plastic should be added 
and the whole covered with 8 oz. canvas sewed on. 

The fittings should be covered with blocks and plastic or with all plastic of a thickness to 
correspond with the covering on the pipe. 

The flanges should be covered with removable flange covering made up of blocks and plastic, 
2" thick on special netting, and covered with canvas to match the pipe covering. 

Exhaust piping, feed piping, drips, etc., should be covered with Standard Sectional Covering 
and with regular canvas jacket. 

For standard thickness of covering apply 45 per cent discount to list given. For fittings apply 
45 per cent. Note that the cost of covering the flanges on an elbow or tee is not included in the 
cost as given for elbow or tee and is to be added. 

For superheated steam lines the 3" thickness is advisable. Figure a discount on 3" thickness 
of 35 per cent. This makes the price of the 3" thickness per lineal foot all installed with canvas 
jacket : 

4" pipe $2.05 for 8" pipe 

5" " 2.37 " 10" " 

6" " 2.67 " 12" " 



^.43 for 
1.63 " 
1.76 " 
1.89 " 



For fittings covered with 3" thickness use regular fitting prices as per list for Standard Thick- 
ness and add 10 per cent. 

Removable flange covers for this thickness of covering would be 2" thick and the cost of these 
covers is not included in the cost of elbows and tees as given in the price list. 

The price of these flange covers installed is 10 per cent above the figures given in the right hand 
column. 

Boiler drums should be covered with blocks 2" thick and 3^" of plastic added. Such covering 
costs 35 cents per square foot area of the external surface of the covering. 



158 



NOTES ON POWER PLANT DESIGN 



For smoke flues, flues leading to economizers, etc., blocks 1" thick should be wired on and cov- 
ered with ^2" of plastic. This costs 25 cents a square foot. 

The outside diameter of 8" pipe is 8.625", the circumference in feet is 2.258. 

The total surface of 200 ft. of pipe is 451.6 sq. ft. and the B. T. U. loss per year is 365 x 24 
X 451.6 X 3 X (468.5 - 68.5) = 4,747,200,000, assuming room to be 68.5° F. 

If 10,000 B. T. U. are utilized by the boiler per lb. of coal burned, the coal required to supply 
this loss would be 474,200 lbs. or 237.1 tons. At $4.50 per ton this amounts to $1067. 

If a covering 3" thick is used, an efficiency of 88 per cent may be assumed. The saving due 
to the covering becomes .88 x 1067 = $939 per year. 

The first cost of the covering would be for the 200 feet of pipe 200 x $2.05 = $410 

10 pairs of flanges 10 x $2.53 = 25.30 



$435.30 



The covering would more than pay for itself in six months. 

The cost of a covering may be figured from the price list, noting the discount given on the 
different items. 



PRICE LIST OF 85% MAGNESIA AND ALL OTHER SECTIONAL COVERINGS 







Price per 




Price per 




Price per 


Inside 


Standard Line al 




Lineal 




Lineal 


Diameter 


Thickness Foot Can- 


Thicliness Foot Can- 


Thickness 


Foot Can- 


of 


of 


vas Jaciceted 


of 


vas Jacketed 


of 


vas Jacketed 


Pipe 


Coveri 


ng 


Covering 


Covering 




'A" 


K' 


$.22 


lA' 


$.46 


2" 


$.75 


H" 


y%' 


.24 


\A' 


.49 


2" 


.80 


1" 


Vs' 


.27 


\A' 


.52 


2" 


. .85 


IH" 


' Vs' 


.30 


lA' 


.56 


2" 


.90 


. Wi" 


%' 


.33 


lA' 


.60 


2" 


.95 


2" 


lA' 


' .36 


lA' 


.64 


2" 


1.00 


2J^" 


lA' 


.40 


IK' 


.70 


2" 


1.05 


3" 


U' 


.45 


lA' 


.76 


2" 


1.15 


3J^" 


lA' 


.50 


lA' 


.82 


2" 


1.25 


4" 


1^'- 


.60 . 


\Vi 


.88 


2" 


1.35 


m" 


1%' 


.65 


lA' 


.94 


2" 


1.45 


5" 


IVs' 


.70 


lA' 


1.00 


2" 


1.55 


6" 


1^' 


.80 


lA' 


1:10 


2" 


1.70 


7" 


IM' 


1.00 


lA' 


1.20 


2" 


1.85 


8" 


IW 


1.10 


lA' 


1.35 


2" . 


2.00 


9" 


IM' 


1.20 


lA' 


1.50 


2" 


2.20 


10" 


IK' 


1.30 


lA' 


1.65 


2" 


2.40 


12"* 


IH' 


1.85 


\A' 


1.85 


2" 


2.70 


14" 


1^' 


2.10 


lA' 


2.10 


2" 


3.00 


16" 


I'A' 


2.35 


m' 


2.35 


2" 


3.30 


18" 


1^' 


2,60 


lA' 


2.60 


2" 


3.60 


20" 


I'A' 


2.85 


lA' 


2.85 


2" 


4.00 


24" 


m' 


3.30 


lA' 


3.30 


2" 


4.50 


30" 


iM' 


4.00 


lA' 


4.00 


2" 


5.50 



*A11 coverings above 10 in. furnished in segment form; jackets not included in the prices. 



NOTES ON POWER PLANT DESIGN 



159 



PRICE LIST OF 85% MAGNESIA AND ALL OTHER SECTIONAL COVERINGS — Cont. 













Block List 




Double 


Price per 




Price per 


Double 


Price per 




Price per 


Layer. 


Lineal 


Double 


Lineal 


Layer. 


Lineal 


Double 


Lineal 


Double 


Foot Can- 


layer. To- 


Foot Can- 


Double 


Foot Can- 


layer. To- 


Foot Can- 


Standard 


vas Jack- 


tal Thick- 


vas Jack- 


Standard 


vas Jack- 


tal Thick- 


vas Jack- 


Thickness 


eted 


ness 3 in. 


eted 


Thickness 


eted 


ness 3 in. 


eted 


m" 


$.65 


3" 


$1.20 


K" 


$.27 


2%" 


$.64 


m" 


.70 


3" 


1.35 


M" 


.27 


2M" 


.68 


iVi" 


.75 


3" 


1.40 


• %" 


.30 


2%" 


.72 


iVi" 


.80 


3" 


1.45 


1" 


.30 


W2" 


.75 


iVi" 


.85 


3" 


1.55 


IH" 


.34 


2%" 


.79 


n 1 II 
■''16 


.90 


3" 


1.65 


IM" 


.38 


2M" 


.83 


2A" 


1.00 


3" 


1.75 


i%" 


.42 


2K" 


.87 


2A" 


1.10 


3" 


1.90 


iy2" 


.45 


3" 


.90 


9 1 // 
•^16 


1.20 


3" 


2.05 


i%" 


.49 


31^" 


.98 


2^" 


1.40 


3" 


2.20 


m" 


.53 


Z'A" 


1.05 


2M" 


1.50 


3" 


2.35 


W%" 


.57 


4 


1.20 


2M" 


1.60 


3" 


2.50 


2" 


.60 






2K" 


1.80 


3" 


2.70 










2>^" 


2.25 


3" 


2.90 










2H" 


2.50 


3" 


3.15 










W2" 


2.70 


3" 


3.40 










2}^" 


2.90 


3" 


3.65 










3" 


4.10 


3" 


4.10 










3" 


4.60 


3" 


4.60 










3" 


5.10 


3" 


5.10 










3'^ 


5.60 


3" 


5.60 










3" 


6.00 


3" . 


6.00 










3" 


7.00 


3" 


7.00 










3" 


8.40 


3" 


8.40 











Sizes 












of 








G. , 


Flange 


Fittings 


Elbows 


Tees 


Crosses 


Valves 


Covers 


¥2" 


$.30 


$.36 


$.48 


$.54 


$.50 


M" 


.30 


.36 


.48 


.54 


.50 


1" 


.30 


.36 


.48 


.54 


.50 


1J€" 


.30 


.36 


.48 


.54 


.50 


iy2" 


.30 


.36 


.48 


.54 


.50 


2" 


.36 


.42 


.54 


.60 


.60 


2J^" 


.42 


.48 


.60 


.78 


.70 


3" 


.48 


.54 


.70 


.96 


.80 


3^" 


.54 


.60 


.80 


1.20 


.90 


4" 


.60 


.75 


.95 


1.50 


1.00 


4K" 


.72 


.90 


1.10 


1.85 


1.30 


5" 


.90 


1.20 


1.50 


2.25 


1.60 


6" 


1.30 


1.60 


2.00 


2.80 


1.90 


7" 


1.80 


2.20 


2.80 


3.60 


2.20 


8" 


2.40 


3.00 


3.60 


4.40 


2.50 


9" 


3.00 


3.80 


4.40 


5.30 


2.90 


10" 


3.60 


4.60 


5.20 


6.20 


3.30 



160 NOTES ON POWER PLANT DESIGN 



SPECIFICATIONS 

The specifications for a Condensing Equipment for a 1500 K. W. Low Pressure Steam Turbine; 
for Automatic Pump and Receiver; for Direct Acting Boiler Feed Pumps and for Turbine Driven 
Centrifugal Boiler Feed Pumps were furnished by Mr. B. II. T. Collins '88. 



SPECIFICATIONS 

FOR 

CONDENSING EQUIPMENT 

Including 

Surface Condenser, Hot Well Pump, Dry Vacuum Pump 

1. Number Wanted. One. 

2. Type. Surface condenser with separate wet and dry air pumps. 

3. Capacity. 

Amount of steam to be condensed, 000 lbs. per hour. 
Temperature of injection water, 70° Fahrenheit. 

Absolute pressure in condenser, 2 inches of mercury or 28 inches vacuum referred to a 
30-inch barometer. 

4. Character of Circulating Water. 

Fresh river water. 

5. Source op Circulating Water. 

From factory water supply system. Any quantity up to 000 gallons per min. at any 
pressure required." 

6. Relative Location of Condensing Equipment and Turbine. 

The surface condenser with the dry air pump will be located directly beneath the horizontal 
turbine to which it will be connected and as near to it as practicable. The wet or hot 
well pump can be located as much below this level as required. The exhaust outlet 
of the turbine will look down. 

7. Equipment to be Furnished. 

The equipment to be furnished includes surface condenser, wet or hot well pump and 
dry air or dry vacuum pump required to give the results stated under "Capacity." 

The hot well pump shall be of the duplex direct-acting steam driven type. 

The dry vacuum pump shall be of the rotative steam driven type. 

The condenser proper, hot well and dry vacuum pumps are described in detail under sep- 
arate specifications following. 



SPECIFICATIONS FOR SURFACE CONDENSER 

1. Number Wanted. One. 

2. Construction. 

This surface condenser shall contain not less than 000 sq. ft. of cooling surface. The shell 
and heads are to be furnished Avith openings for the exhaust steam, circulating water 
inlet and discharge, dry air and condensed steam, of sizes and locations approved by 
the Engineer. 



NOTES ON POWER PLANT DESIGN 161 

The tube heads are to be of rolled brass. 

The tubes are to be seamless drawn brass of the following composition : 

Copper 60% 

Zinc 40% 

Every tube is to be inspected for faults on both inside and outside and all tubes show- 
ing any indication of imperfection of any kind are to be rejected. 

The condenser is to be tested under 25 lbs. per sq. in. cold water pressure applied in both 
steam and water spaces before shipment from the factory and made tight. 

The interior of the shell is to be carefully painted with two coats of anti-rust metallic paint. 
The whole exterior is to be scraped, filled and painted with the best lead and oil paint 
before leaving the shops. 

All interior bolting in contact with the circulating water is to be of composition unless 
otherwise specified. 

3. Bolts, Etc. 

Bolts, nuts and screws shall be of the United States standard. 

4. Finish. 

All castings shall be carefully dressed down, filled and painted with the best quality of 
paint. 

5. Drilling. 

All flanges shall be faced and drilled in accordance with Manufacturers' Standard for flanges 
and drilling. 

6. Design, Material and Workmanship. 

The design shall be such as to insure safe, reliable and economical operation. 

The material and workmanship shall be the best of their respective kinds. 

The contractor shall furnish, without charge, F. O. B. cars, a duplicate of any part that 

may prove defective in material or workmanship within one year after the condensing 

equipment has been started. 

7. Drawings. 

Bidder shall submit in connection with his proposal an outline drawing to scale and a 
description of the condenser he proposes to furnish, giving in detail the design, and 
arrangement made for removal of parts and for repairs. 

8. Condenser Data. 

The bidder shall furnish the following data on each condenser: 

Number of tubes 

Length of tubes ft in. 

Outside diameter of tubes in. 

Thickness of tubes No. 18 B. W. G. 

Thickness of tube heads in. 

Cooling surface sq. ft. 

Material of tubes 

Area exhaust opening 

Size of circulating water inlet opening in. 

Size of circulating water discharge opening in. 

Size dry air opening in. 

Approximate finished weight lbs. 

Approximate shipping weight lbs. 



162 NOTES ON POWER PLANT DESIGN 

SPECIFICATION FOR DIRECT ACTING HOT WELL PUMP 

1. Number Wanted. One. 

2. Type. Horizontal duplex piston type. 

3. Kind of Service. 

Removing condensed steam from surface condenser. 

4. Working Steam Pressure. 175 lbs. per sq. in. gage. 

5. Minimum Steam Pressure. 125 lbs. per sq. in. gage. 

6. Steam Temperature. 527.6° F. (approx.) or 150° superheat. 

7. Back Pressure. 17 lbs. per sq. in. absolute. 

8. Discharge Water Pressure. Not over 15 ft. head. 

9. Capacity. 

The pump shall be capable of delivering at least gallons of water per minute under 

the conditions of operation as described in this specification. 

10. Water End Fittings. 

Bronze cylinder linuigs, piston rods, pistons, stuffing box glands, valve seats, bolts, plates 
and springs. Hard rubber valves for 212° F. water. 

11. Lubrication. 

There shall be furnished with the pump one (1) pint "Detroit" lubricator. 

12. Drilling. 

All flanges shall be faced and drilled in accordance with Manufacturers' Standard for flanges 
and drillings. 

13. Material and Workmanship. 

The material and workmanship shall be the best of their respective kinds. The Contractor 
shall furnish without charge F. O. B., a duplicate of any part that may prove defective 
in material, or workmanship one year after the pump has been started. 

14. Drawings. 

Bidder shall submit in connection with his proposal, an outline drawing to scale and a de- 
scription of the pump he proposes to furnish, giving all necessary details. 

15. Pump Data. 

Bidder shall furnish the following data on the pump: 

Diameter steam cylinder ins. 

Diameter water cylinder ins. 

Length of stroke ins. 

Diameter steam inlet ins. 

Diameter exhaust outlet . ins. 

Diameter suction ins. 

Diameter discharge ins. 

Approximate finished weight lbs. 

Approximate shipping weight lbs. 

SPECIFICATION FOR ROTATIVE DRY VACUUM PUMP 

1. Number Wanted. One. 

2. Type. 

Horizontal, crank and fly wheel rotative dry vacuum pump. 

3. Kind of Service. 

Removing non-condensible vapors from condenser. 

4. Speed. 

Not over 150 R. P. M. Piston speed not over 300 feet per minute. 

5. Working Steam Pressure. 175 lbs. per sq. in. gage. 

6. Minimum Steam Pressure. ' 125 lbs. per sq. in. gage. 

7. Steam Temperature. 527.6° F. (approx.) or 150° superheat. 



NOTES ON POWER PLANT DESIGN 163 

8. Back Pressure. 17 lbs. per sq. inch absolute. 

9. Capacity. 

The capacity of this air pump shall be at least 35 times the volume of the condensed steam. 

10. Cylinders. 

The cylinders shall be of close-grained cast iron. 

The air cylinder shall be strong enough to withstand a normal working pressure of 50 lbs. 
per sq. in. and the steam cylinder shall be strong enough to withstand a steam pressure 
of 200 lbs. per sq. in. after being rebored ]/i" in diameter without causing the tensile 
strength in the metal to exceed 2500 lbs. per sq. in. The steam cylinder shall be lagged 
with 85% carbonate of magnesia held on with Russia iron covering. Provision shall 
be made on both the steam and air cylinders for attaching indicators. All cylinders 
shall be provided with drip cocks. The steam and air ports shall be of ample size to 
allow easy and quick action of the steam and air. All parts shall be so arranged as 
to be readily accessible. 

11. Steam Valves and Valve Motion. 

Throttle valve will be furnished by the purchaser. 

The steam valve shall be of the balanced type with provision for taking up wear. 

12. Air Valves. 

The air valves shall be of a suitable type for obtaining the greatest vacuum under the 
conditions herein specified. 

13. Lubrication. 

Ample lubrication shall be provided for all parts subject to wear. There shall be fur- 
nished with pump one (1) nickle plated, 2 qt., two feed Richardson sight feed lubri- 
cator with divided reservoir for supplying two different kinds of oil, one for the steam 
cylinder and the other for the air cylinder. 

14. Wrenches. 

One full set of wrenches shall be furnished with the pump. 

15. Bolts, Etc. 

Bolts, nuts and screws shall be of the United States standard. 

16. Finish. 

The working parts of the pump shall be highly finished, all exposed metal parts usually 
polished, such as cylinder cover and the faces of flywheels, shall be smooth turned, and 
together with all castings carefully filled and painted ^^ith the best quality of paint. 

17. Drilling. 

All flanges shall be faced and drilled in accordance with Manufacturers' Standard. 

18. Design, Material and Workmanship. 

The design shall provide ample bearing surfaces, abundant lubrication and strong ruggeil 
parts and shall insure safe, reliable and economical operation. 

The material and workmanship shall be the best of their respective kinds. The contractor 
shall furnish without charge f. o. b. a duplicate of any part that may prove defective 
in material or workmanship within one year after the pump has been started. 

19. Drawings. 

Bidder shall submit in connection with his proposal, an outline drawing to scale and a 
description of the pump he proposes to furnish, giving in detail the design of pistons, 
plungers, valves, and arrangement made for removal of parts and for repairs. 

20. Pump Data. 

Bidder shall furnish the following data on the pump : 
Dimensions : 

Diameter steam cylinder ins. 

Diameter air cylinder ins. 

Length of stroke ins. 



164 NOTES ON POWER PLANT DESIGN 

Floor Space: 

Length ft ins. 

Width ft. ins. 

Height ft ins. 

Pipe Opening: 

Steam ins. Suction ins. 

Exhaust ins. Discharge ins. 

Steam End: 

Type of steam valve 

Area admission ports sq. ins. 

Area exhaust ports sq. ins. 

Air End: 

Type of air valve 

Area admission ports sq. ins. 

Area exhaust ports sq. ins. 

Bearings : 

Diameter main bearings ins. 

Length main bearings ins. 

Diameter crank pin ins. 

Length crank pin . ins. 

Diameter wrist-pin ins. 

Length wrist-pin ins. 

Diameter of shaft ins. 

Dimensions of cross-head shoes ins. 

Governor: 

Type of governor 

Flywheel: 

Diameter ft ins. 

Width of face ins. 

Approximate Weights: 

Finished weight lbs. 

Shipping weight lbs. 



SPECIFICATION FOR 1500 K. W. MAXIMUM RATED HORIZONTAL LOW PRESSURE 

STEAM TURBINE 

Steam End 

1. Number Wanted. One. 

2. Type. Horizontal low pressure condensing. 

3. Kind of Service. Direct cormected to generator supplying current for factory motors 

and motor-generators or rotaries. 

4. Speed. Revolutions per minute. 

5. Steam Pressure at Throttle. Fifteen pounds absolute. Alternate proposition on turbine 

suitable to use both fifteen poimds absolute and 175 pounds per sq. in. gage. 

6. Steam Temperature at Throttle. Temperature due to pressure given above. No super- 

heat. 

7. Back Pressure. 2" of mercury absolute. 

8. Regulation. The speed of the turbine shall not vary more than 23^^% above or below 

the normal speed at any load less than 500 K. W. Maximum speed variation where 
full load is thrown on or off instantaneously will not exceed %. The con- 
tractor shall furnish as part of the turbine an electrical synchronizing device for vary- 
ing the speed of the turbine from the switchboard. 



NOTES ON POWER PLANT DESIGN " 165 

9. Capacity. When operating condensing under the condition herein stated the turbine shall 
furnish power to generate, — - 

1500 K. W. continuously; 
2000 K. W. momentarily. 

10. Throttle Valve, ^he throttle valve shall be of the Schutte and Koerting make, actuated 

at a speed of 10% above normal by a safety governor. 

11. Bolts, Nuts, Etc. Bolts, nuts and screws shall be of the United States Standard. 

12. Finish. The turbine as a whole shall be highly polished, all exposed metal parts polished 

and castings carefully dressed down, filled and painted with the best quality of paint. 

13. Drilling. All flanges shall be faced and drilled in accordance with Manufacturers' Standard 

for flanges and drilling. 

14. Steam Consumption. The turbine shall consume not more than the amoimts of steam 

given below when developing the corresponding kilowatts, running at a speed of 

revolutions per minute, with a steam pressure of fifteen pounds absolute per sq. in. and 
exhausting against a back pressure of 2 inches of mercury absolute. The steam pressure 
shall be the averaged measured just outside the throttle valve, and the back pressure 
shall be measured in the exhaust pipe near the turbine. 

Steam Consumption Pounds per K. W. hour 

K. W lbs. per K. W. H. 

375 lbs. per K. W. H. 

750 lbs. per K. W. H. 

1125 lbs. per K. W. H. 

1500 lbs. per K. W. H. 

15. Erection. The contractor shall provide for the superintendence of erection of the turbine, 

all common labor to be provided by the purchaser. The contractor agrees to have the 
turbine and generator erected ready for operation within 15 days after their arrival at 
destination provided no delays are caused by the purchaser. 

16. Design, Material and Workmanship. The design shall provide ample bearing surfaces, 

abundant lubrication and strong rugged parts, and shall insure safe, reliable and econo- 
mical operation, and without undue heating or vibration. The material and workman- 
ship shall be the best of their respective kinds. The contractor shall furnish, without 
charge, f. o. b., a duplicate of any part that may prove defective in material or work- 
manship within one year after the turbine has been started. 

17. Drawings. Bidder shall submit in connection with his proposal an outline drawing to scale 

and a description of the turbine he proposes to furnish, giving in detail the arrange- 
ments made for the removal of parts for repairs. 

18. Turbine Data. Bidder shall furnish the following data on the turbine: 

Dimensions : 

Length 

Width 

Height 

Piping : 

Steam 

Exhaust ". 

Weight: 

Weights of heaviest part 

Weight of heaviest part to be moved when mak- 
ing ordinary repairs 

Shipping weight 

Finished weight 



166 NOTES ON POWER PLANT DESIGN 

GENERATOR END 

1. Number Wanted. One. 

2. Type. Revolving field. 

3. Kind op Service. Supplying current for factory motors and motor-generators or rotaries. 

4. Speed. Revolutions per minute 

5. Number op Poles 

6. Frequency. 60 cycles per second. 

7. Phase. Three phase. 

8. Voltage. 480 at no load. 

480 at full load, 80% power factor. 

9. Regulation. The regulation of generator when operating at 100% load and 80% power 

factor shall not exceed %. By "regulation" is meant the rise in 

potential of generator when specified load at specified power factor is thrown off. 

10. Capacity. The generator shall develop: 

1500 K. W. continuously. 
2000 K. W. momentarily. 
Generator shall be capable of developing K. W. as above, at voltage specified above and 
at any power factor not less than 80%. 

11. Amperes. Full load current amperes per phase. 

12. Temperature Rise. Shall not exceed the following: 

When generating continuously at 1500 K. W. 

480 volts. 

80% Power Factor. 
Field and armature by thermometer 50 deg. C. 

Collector rings and brushes by thermometer 50 deg. C. 
Bearings and other parts by thermometer 50 deg. C. 

13. Style op Field Winding. Separately excited. 

14. Excitation. Excitation of separately excited fields shall be by direct current at 125 V. It 

shall not be necessary to raise excitation above 125 V. in order to maintain voltage spec- 
ified above on the generator with 1500 K. W. load and 80% power factor. 

15. Rheostat. A hand operated rheostat shall be furnished in field circuit to control the voltage. 

16. Field Discharge Resistance. A suitable field discharge resistance shall be furnished. 

17. Rheostat Mechanism. The generator field rheostat shall be furnished with hand wheel 

and chain operating mechanism suitable for mounting on switchboard panel. 

18. Parallel Operation. The generator shall be designed so that it may be operated in parallel 

with other machines of similar type, of the same or different size, or inductive or non- 
inductive loads without seriously disturbing the regulation of any of the machines, or 
affecting the lights on the line. 

19. Insulation Test. The ohmic resistance and dielectric strength of the insulation shall meet 

the requirements of the latest report of the Committee on Standardization of the Amer- 
ican Institute of Electrical Engineers. 

20. Generator Data. Bidder shall furnish the following data on generator: 

■ Maximum voltage that can be obtained from generator at 100% load and 80% power 

factor will be volts. 

The commercial efficiency of the generator will be as follows: 

% at 3^ load. 

% at 3/i load. 

% at ^ load. 

% at full load. 

Exciting current at full load and 80% power factor will be amperes at 

125 volts. Maximum current on short circuit will be. amperes at unity 

power factor. Shipping weights will be as follows: 

Rotor pounds. 

Generator complete pounds. 

Heaviest piece pounds. 



NOTES ON POWER PLANT DESIGN 167 

SPECIFICATION FOR DIRECT ACTING BOILER FEED PUMPS 

1. Number. Two. 

2. Type. Horizontal duplex outside packed plunger. 

3. Service. Boiler feed. 

4. Working Steam Pressure. 175 lbs. per sq. inch gage. 

5. Working Exhaust Pressure. 17 lbs. absolute. 

6. Working Discharge Water Pressure. 250 lbs. per sq. inch. . 

7. Working Suction Head. 8 ft. above floor on which pump stands. 

8. Temperature of Water. 212 deg. F. 

9. Capacity. Normal capacity 250 gallons per minute for each pump. Maximum capacity 

500 gallons per minute for each pump. 

10. Water End Fittings. Hard, close-grained cast iron plungers, composition covered, bronze 

stuffing box glands, valve seats, and valves of the pot valve type. 

11. Air Chambers of proper capacity and length to be furnished for both suction and discharge 

connections. 

12. Proposal. Make proposal f. o. b.. .stating price; time before shipment; shipping weight; 

and enclose print showing general dimensions and sizes of all connections. 

SPECIFICATION FOR TURBINE DRIVEN CENTRIFUGAL BOILER FEED PUMPS 

1. Type. Multistage Centrifugal Pumps, direct connected to Steam Turbines, on common 

bed plate with flexible shaft coupling. 

2. Number. Two. 

3. Service. Boiler Feed. 

4. Maximum Capacity. 500 gallons per minute for each pump. 

Capacity for most economical steam consumption, — 250 gallons per minute for each 
pump. 

5. Working Discharge Water Pressure. 250 pounds per square inch. 

6. Working Suction Head above Center of Pump Shaft. 8 ft. of water. 

7. Working Steam Pressure. 175 lbs. per square inch, gage. 

8. Working Exhaust Pressure. 17 lbs. absolute. 

9. Make Proposal f.o. b.. .stating price; time before shipment; shipping weight; print showing 

general dimensions and sizes of all connections; guaranteed steam consumption of tur- 
bine at maximum rating of 500 gallons per minute, also at 250 gallons per minute in 
pounds per H. P. per hour and efficiency of pump at each of above capacities. 

SPECIFICATION FOR AUTOMATIC PUMPS AND RECEIVERS 

1. Number. Five. 

2. Type. Alternate propositions on (1st) single cylinder direct acting piston type steam pump 

with receiver and automatic arrangement for starting and stopping pump and (2nd) 
horizontal duplex piston type with receiver and automatic arrangement for starting and 
stopping pump. 

3. Service. Returning hot water drips from trap discharges, heating and curing systems, etc., 

to open feed water heater. 

4. Working Steam Pressure. Maximum 100 per sq. inch; minimum 20 per sq. inch. 

5. Working Exhaust Pressure. 17 absolute. 

6. Working Discharge Water Pressure. Not over 40 ft. head including pipe friction. 

7. Working Suction Head. Gravity and trap returns to receiver. 

8. Temperature of Water. 150 deg. F. to 212 deg. F. 

9. Capacity. Four pumps 60 gallons per minute and the fifth pump 100 gallons per minute. 



168 NOTES ON POWER PLANT DESIGN 

10. Water and Fittings. Three 60-gallon and one 100-gallon pumps bronze cylinder linings, 

piston rods, pistons, stuffing box glands, valve seats, bolts, plates and springs. Hard 
rubber valves for 212 deg. F. water. Water piston to have metallic packing rings and 
also to be arranged for the use of fibrous packing if desired. One 60-gallon pump and 
receiver to be iron fitted throughout, no bronze whatever. (For use with water contain- 
mg sulphur.) 

11. Proposal. Make proposal stating price for both sizes of pumps in both single and duplex 

types; also 60-gallon pump and receiver iron fitted throughout; time before shipment; 
shipping weights; prints showing general dimensions and sizes of all connections and 
details of float and steam regulating valve with connections between them. 

SPECIFICATIONS FOR 30" x 60" x 60" HORIZONTAL CROSS-COMPOUND NON- 
CONDENSING CORLISS ENGINE 

1. Number Wanted. One. 

2. Type. Horizontal Corliss, cross-compound, non-condensing. 

3. Kind of Service. Rope drive to factory line shafting. Exhausting to low pressure steam 

turbine. 

4. Indicated Horse Power: 

At lowest steam consumption 

At maximum load 

5. Speed. 80 revolutions per minute. 

6. Steam Pressure at Throttle. 175 lbs. per sq. in. gauge. 

7. Steam Temperature at Throttle. 377° F. 

8. Back Pressure. 17 lbs. per sq. in. absolute. 

9. Point of Cut-off: 

At lowest steam consumption % 

At maximum load % 

10. Regulation. The speed of the engine shall not vary more than 2]/2 per cent above or below 

the normal speed at any load less than indicated horse power. 

11. Cylinder Sizes. The dimensions of the cylinder shall be as follows : 

Diameter Stroke 

High pressure cylinder 30" 60" 

Low pressure cylinder 60" 60" 

12. Hand. The engine shall be right hand, that is, when standing at the high pressure cylinder and 

looking toward the shaft, the wheel will be on the right and the low pressure cylinder on the 
right of the wheel. 

13. Wheel. The wheel shall have 40 grooves for 1^" rope and be 18 ft. in diameter. 

14. Cylinders. The cylinders shall be of close-grained cast iron strong enough to withstand 

200 lbs. steam pressure per sq. in., after being rebored %" in diameter without caus- 
ing the tensile strength in the metal to exceed 3500 lbs. per sq. in. 
It shall be lagged with 85% carbonate of magnesia held on with Russia iron covering. 
Provision shall be made on the cylinder for attaching indicators, and an indicator re- 
ducing motion shall be provided as part of the engine. The cylinder shall be provided 
with drip cocks. The steam ports shall be of ample size to allow easy and quick action 
of the steam. • 

15. Valves. The cylinder shall be provided with relief valves of ample size and at suitable 

position to protect the engine from damage due to water. 
Throttle valve shall be furnished with the engine. 
The steam valves shall be of the Corliss type with separate eccentrics for the steam and 

exhaust valves. 



NOTES ON POWER PLANT DESIGN 169 

16. Governors. The governor for the engine shall be of the flyball type. 

17. Lubrication. Lubrication shall be by means of sight feed oil cups which shall be accessibly 

located and shall positively and continuously supply the main shaft bearings, crank pins, 
wrist pins, guides, valve parts, etc. with oil. These oil cups shall be provided with 
bottom connections piped to a common point ready for connection to a gravity oiling 
system. All pipe shall be semi-annealed iron pipe size brass pipe. All brass parts shall 
be polished and nickel plated. 

Grease cups will be allowed only on eccentrics. 

Two Richardson model "M" four-feed oil pumps shall be furnished for the cylinders. 

18. Wrenches and Drawings. The following fittings shall be furnished with the engine: 

1 set of forged steel wrenches. 

Foundation plans for setting foundation bolts. , 

Drawings showing dimensions of engine and foundation. 

19. Packing. The piston rod shall be packed with metallic packing and the 

valve stems with metallic packing. 

20. Bolts, Etc. Bolts, nuts and screws shall be of the United States standard. 

21. Finish. The engine as a whole shall be highly finished, all exposed metal parts polished and 

castings carefully dressed down, filled and painted with the best quality of paint. 

22. Drilling. All flanges shall be faced and drilled in accordance with Manufacturer's Standard. 

23. Steam Consumption. The engine shall consume not more than the amounts of steam shown 

below for each load when running at a speed of 80 revolutions per minute with a steam 
pressure of 175 lbs. per sq. inch above the atmosphere at a temperature as indicated below 
and exhausting against a back pressure of 17 lbs. per sq. inch absolute. The steam pres- 
sure shall be the average measured just outside the throttle valve and the back pressure 
shall be measured in the exhaust pipe near the engine. 

Steam Consumption in Pounds per I. H. P. 
Load I. H. P. Saturated Steam 

M 



Full 

24. Erection. The engine shall be erected by the Contractor on foundation furnished by the 

Purchaser. After the engine arrives at destination the Contractor agrees to push the 
erection through with all reasonable promptness, working a full day force. The engine 
is to be erected ready for operation within 30 days after its arrival at destination. 

25. Design, Material and Workmanship. The design shall provide ample bearing surfaces, 

abundant lubrication and strong rugged parts and shall insure safe, reliable and econo- 
mical operation, and without undue heating or vibration. 

The material and workmanship shall be the best of their respective kinds. The Contractor 

shall furnish, without charge, f . o. b a duplicate of any part that may 

prove defective in material or workmanship within one year after the engine has been 
started. All nuts on cylinder heads, bonnets and other parts which are subject to re- 
moval shall be case-hardened. 

All connections about the engine shall be made perfectly tight and all parts of the engine 
made as accessible as possible and capable of ready removal for repair or replacement. 
All parts of the engine subject to wear shall have means provided for taking up such 
wear. All interchangeable parts shall be machined to gauge. 

26. Drawings and Data. Bidder shall submit in connection with his proposal an outline 

drawing to scale and a description of the engine he proposes to furnish, giving in detail 
the design of cylinder, piston, governor, bearings and arrangement made for removal 
of parts and for repairs. 



170 



NOTES ON POWER PLANT DESIGN 



27. Engine Data. Bidder shall furnish the following data on the engine: 
Floor Space 

Length ft inches 

Width ft inches 

Height ft inches 

Piping 

H. P. Cyl. L. P. Cyl. 

Steam inches 

Exhaust inches 

Valves 

Type of steam valves " 

Area admission ports sq. in. 

Area exhaust ports sq. in. 

Connecting Rods 

Type 

Length inches 

Bearings 

Diameter main bearings 
Length main bearings 

L.P. 
L.P. 
L.P. 
L.P. 



Diameter crank pin 


H.P. ... 




Length crank pin 


H.P. ... 




Diameter wrist pin 


H.P. ... 




Length wrist pin 


H.P. ... 




Diameter of shaft 






Dimensions of cross- 


head shoes . 




Governor 




Type of governor 






Belt Wheel 






Diameter 


18 ft. 


inches 


Width of face 




56 inches 


Weights 






Weight of heaviest part 


lbs. 


Weight of fly-wheel 




lbs. 


Shipping weight of engine 


lbs. 


Finished weight of engine 


lbs. 



NOTICE TO CONTRACTORS 
Steam Driven Centrifugal Pumping Unit for the City of. 



Sealed proposals and bids for furnishing to the City of Mass., 

and installing in the St., Pumping Station of the City of 

a steam turbine driven centrifugal pumping outfit, as hereinafter described, will be received by 

the Commission of Water and Water Works of at the City Hall, 

Mass., until 12m, September , 1913. 

Bids must be made in duplicate. 

Each bidder must leave with his bid a properly certified check for the sum of two thousand 

dollars ($2,000) payable to the order of the City of , which check will be returned to the 

bidder unless forfeited as hereinafter provided. 

A bond will be required, for the faithful performance of the contract, in the sum of ten thousand 
dollars ($10,000) of an approved surety company doing business in Massachusetts. 

The bidder is requested to name the surety company which will sign his bond in case the con- 
tract is awarded him. 



NOTES ON POWER PLANT DESIGN 171 

If notice of the acceptance of the bid shall, within twenty days after September , 

1913, be given to the bidder by the Commissioner of Water and Water Works of , 

the bond must be fm'nished within six days (Sunday excepted) after such notification; and in 
case of the failure of the bidder after such notification to furnish the bond within said time the 
bid shall be considered as abandoned and the certified check accompanying the bid shall be for- 
feited to the city. 

Each bidder is to furnish with his bid detailed description and specifications covering the appar- 
atus he purposes to install. 

He is to give also the duties (duty is here considered as the foot-pounds of water work done 
per million British Thermal Units) he will guarantee. 

First considering the steam used by the steam turbine alone without including the steam used 
by either wet or dry pumps used in connection with the condensing outfit, and 

Second including the steam used by these pumps with the turbine steam. The guarantees 
of duty to be made on a pressure at the throttle of 125 lbs. gage and on steam containing not more 
than one and one-half per cent moisture. 

The temperature of the returns to the boiler to be taken the same as the temperature of the 
condensed steam leaving the condenser. If the exhaust steam from the wet and dry pumps is 
sent through a feed water heater and used to heat the 'steam condensed from the turbine on its 
way to the boiler, the temperature of the returns will be taken as the temperature of this feed 
water. The temperature of the suction water to be taken at 70°. The conditions as to head and 
capacity to be taken as hereinafter outlined. 

Each bidder is to furnish dimensioned drawings giving the general outside measurements 
of the entire apparatus when assembled together with such drawings or cuts as may be necessary 
to show the construction of his apparatus. 

The one to whom the contract is awarded is to furnish the city with a working drawing of 
the foundation (to be built by the City) and complete working drawings of the turbine centri- 
fugal pumps and condensing outfit complete. 

The bidder is to guarantee that all bearings and reduction gears if used will be continuously 
lubricated and will run continuously without over-heating. 

The bidder is to agree to make at his own expense all repairs which may be made necessary 
through original faulty construction, design or workmanship for a period of six months after the 
unit goes into regular service. 

Neither experimental nor unusual types of apparatus will be considered. 

Each bidder must be prepared to prove to the satisfaction of the Commissioner that he has 
previously installed units of the type he purposes to furnish and he shall state where such units 
are in successful operation. 

The bidder must state the general type design and builders name of any part of the unit which 
is not built at the works of his own company. 

The bidder must give the date of delivery and the time required for the erection of the com- 
pleted plant. 

Payments will be made as follows : Fifty per cent of the contract price ten days after the de- 
livery of the turbine, pumps, condensers, and accessories at the pumping station and the balance 
due the contractor ten days after the acceptance of the unit by the City. 

The Commissioner reserves the right to reject any or all bids or to award the contract as he 
deems best. 

The duty guaranteed, the general design and accessibility of the parts, together with the cost, 
will be considered in awarding this contract. 

Bids in which the duty guaranteed per 1,000,000 British Thermal Units including the steam 
used by the condensing apparatus, falls below 92,000,000 foot-pounds will not be considered. 

The bidder will submit his bid and his specifications on his own printed forms and will add to 
the same the following: 

The Contractor will indemnify and save harmless the City from all claims against the City 
by mechanics, laborers, and others, for work performed or materials furnished for carrying on the 
contract. 

The Contractor will indemnify and save harmless the City, its agents and employees, from all 



172 NOTES ON POWER PLANT DESIGN 

suits and claims against it or them, or any of them, for damages to private corporations and indi- 
viduals caused by the construction of the work to be done under this contract; or for the use of any 
invention, patent, or patent right, material, labor or implement by the contractor, or from any 
act, omission or neglect by him, his agents, or employees, in carrying on the work; and the Con- 
tractor agrees that so much of the money due to him under this contract as may be considered 
necessary by the Comtnissioner may be retained by the City until all such suits or claims for damages 
as aforesaid shall have been settled and evidence to that effect furnished to the Commissioner. 

The Contractor agrees to do such extra work as may be ordered in writing by the Commis- 
sioner, and to receive in payment for the same its reasonable cost as estimated by the Commis- 
sioner plus fifteen per cent of said estimated cost. 

The Contractor agrees to make no claims for compensation for extra work unless the same 
is ordered in writing by the Commissioner. 

The Contractor still further agrees that the Commissioner may make alterations in the work, 
provided that if such changes increase the cost, the contractor shall be fairly remunerated and in 
case they diminish the cost the proper deduction from the contract price shall be made — the amount 
to be paid or deducted to be determined by the Commissioner. 

General Description of Pumping Unit 

A steam driven turbine either directly connected to a centrifugal pump or connected through 
reduction gears and having a smaller stage centrifugal connected by friction clutch or other suit- 
able device to the end of the pump shaft or to one end of the turbine shaft all mounted on a suit- 
able bed plate is to be installed together with a water works type condenser and necessary wet and 

dry pumps in the St. Pumping Station of the City of A feed water 

heater using the exhaust steam of the wet and dry pumps may be installed by the contractor (the 
one to whom the contract is awarded is hereinafter designated as the Contractor) if hereby he is 
able to increase the duty by raising the temperature of the returns. 

This equipment is to be put in the ell at the back of the building which ell is now used as _a 
coal pocket and storage room. There is now a large outside door at the end of the ell leading from 
the back yard into the basement of this building. Another large door located over this basement 
door at the level of the present engine room floor is to be made by the city. The turbine will have 
to be taken in through this new door and the condensing equipment through the basement door. 

This outfit is to be erected and installed by the Contractor on a foundation built by the City 
in accordance with drawings furnished by the Contractor. (Foundation bolts are to be furnished 
by the Contractor.) The Contractor is to temporarily strengthen any floors, coal pockets, etc. 
he may move his machinery over and to take all responsibility during the erection of the machinery. 
Under no circumstances is the operation of the pumping station to be interfered with. 

The City will bring steam to the throttle of the turbine. The throttle valve and safety throttle 
are to be furnished and erected by the Contractor. The City will connect the "suction" pipe with 
the intake of the condenser and will make all connections to the force mains back to the discharge 
end of the centrifugals. In preparation for tests of this unit the City will install a Venturi meter 
in each of these force mains. The Contractor is to pipe the condensed steam back to the boiler 
feeding apparatus and to make all other connections, not specifically referred to. 

The Contractor is to provide, connect, and put in place suitable 8}^" polished brass gages 
with gage cocks as follows, all mounted on a gage board of mahogany or stone fastened to the 
wall of the room at some point to be designated by the chief engineer of the station. 

Gage for pressure at throttle to be divided to 150 lbs. by one pound marks. 

Gage pressure in condenser: this to be a combination pressure and vacuum: 20 lbs. pressure. 

Gage for measuring pressure in force mains of large centrifugal: 120 lbs. by 1 pound marks. 

Gage for measuring pressure in force mains of small centrifugal: 150 lbs. by 1 lb. marks. 

Gage for showing pressure of water at intake to condenser: 50 lbs. by 1 pound marks. 

A clock in a case like the gages is to be fm-nished by the Contractor and mounted on this gage 
board. 

The Contractor is also to provide, connect, and put in place, a mercviry column for measuring 
the vacuum in the condenser and thermometers m suitable wells for determining the temperature 



NOTES ON POWER PLANT DESIGN 173 

of the water entering the condensers, the temperature in each force main and the temperature of 
the returns from the condenser to feed pumps. 

Water comes to these pumps at what has been called the "suction" side under a static head of 
about 23 feet, the head depending upon the level in Breed's Pond. In making calculations for 
duty an average value of the static head of 23 feet at the level of the main floor in the present sta- 
tion may be assumed. The pipe leading from Breed's Pond to the Street Station is about 

one-half mile in length and is 36" in diameter for the first third of the distance and 30" for the 
remaining two-thirds of the distance. There are four elbows in this 30" line. 

The centrifugal directly connected or connected through reduction gears to the turbine shaft 
is to discharge 13,000,000 U. S. gallons in 24 hours into a 30" force main about one-half mile long ■ — 
practically a straight run of pipe. The static pressure at the level of the station floor of the main 
station is 60 lbs. The present pumping outfit is discharging water through this pipe at the rate 
of 10,000,000 gallons in 24 hours. 

The stage centrifugal, connected to the turbine shaft or pump shaft by a friction clutch or other 
suitable device is to deliver 2,000,000 U. S. gallons in 24 hours to a stand pipe through about one- 
half mile of pipe; the first half of which is 16" diameter and the last half 12" diameter; all of cast 
iron. The static pressure at the level of the station floor of the main station is 105 lbs. Drawings 
of the pipe lines can be seen at the office of the City Engineer, City Hall, , Mass. 

The two pumps will be run together the greater part of the time, the high pressure pump con- 
nected and disconnected by means of a clutch or other suitable device without stopping the turbine. 

The water coming from Breed's Pond to the Street Station varies in tem- 
perature from 35° to 80°. A temperature of 70 degrees seems a fair average. The boilers now 
installed are to furnish the steam for this unit. These boilers are of the horizontal Multitubular 
type; two in number working at 125 lb. gage. The steam from these boilers may be considered 
to contain not more than 13^ per cent moisture. The condenser is to be made strong enough 
to stand with safety 105 lb. gage pressure on the water side and 20 lb. gage pressure on the steam 
side. 

A 2" safety valve with whistle is to be attached to the steam side of the condenser. 

The turbine is to be provided with a safety throttle quick operating trip or other suitable 
device, satisfactory to the commissioner to prevent speeding. 

The turbine is to be provided with an outboard exhaust through a water sealed automatic 
relief valve. The discharge from this valve to be carried by means of spiral riveted pipe through 
the roof. The opening made in the roof for this pipe is to be properly flashed with copper and 
made tight against rain and snow. 

To allow for expansion there is to be a flexible connection in the piping between the turbine 
and the condenser. 

The pump impellers are to be of bronze on suitable non-corrosive material and unbalanced 
end thrust on the impellers to be avoided as far as is possible. 

The impeller shafts are to be protected from corrosion by removable sleeves of composition. 
Composition packing glands and bronze studs are to be provided for the pumps. 

The contractor is to paint all machinery and piping erected by him. Such castings as are in 
sight from the floor of the engine room are to be made smooth, nicely fitted at all joints and flanges, 
filled with a proper paint filler and painted and striped in such colors as the commissioner may 
direct. 

The Contractor is to remove all blocking, tools or other material used by him in erecting and 

installing his work and to remove all debris of any nature, in and around the Street 

Pumping Station, produced by him in carrying out this contract. 



174 NOTES ON POWER PLANT DESIGN 

SPECIFICATIONS FOR AND DESCRIPTION OF PUMPING UNIT FOR 

Location. The pumping unit is to be installed in a new building distant about 500 feet north 
from the pumping station on Pond now supplying the City of 

Floor Level. The building will be located on the shore of the pond. The pump room floor being 
from 4 to 7 feet above the level of full pond. 

Pump Motor. The pump is to be either a single or two stage centrifugal, driven by a 4000 volt 
three phase, 60 cycle alternating current motor of the external resistance, slip ring type com- 
plete with device for lifting brushes and short circuiting rings after the pump is up to speed, 
and all necessary starting equipment. 

Motor. The motor must be so designed that the starting current, under given load, will not 
exceed full load running current. 

Motor Characteristics. The temperature rise of the motor when operating at normal rating 
with a room temperature of 25° C. is not to exceed 40° C. 

Electrical Switchboard. A switchboard of slate with dull black finish with the following 
equipment is to be furnished and erected, all meters in black finish. 

(1) One voltmeter with scale calibrated to show 4000 volts. 

(2) One indicating watt meter. 

(3) One ammeter with switch to show current on any of the three phases. 

(4) One kilowatt hour meter. 

(5) Suitable testing terminals to enable check to be made on these instruments. 

(6) Available space for the instruments of the Electric Light Co. which will 

be one kilowatt hour meter and suitable testing terminals. 

(7) Complete switch-operating mechanism and mounting for all switches necessary 

for starting and controlling the motor. The oil circuit breaker to be of remote 
mechanical control type. 

(8) Necessary current and potential transformers for preceding equipment; also available 

space and mounting for the necessary current and potential transformers fur- 
nished by the Electric Light Co. 

(9) A 125-volt switch to control electrically operated discharge valve if such electrically 

operated valve is used; provision shall also be made for 125 volt lighting. 

Lightning Protective Apparatus. In addition to the preceding the following are to be fur- 
nished and separately mounted: One complete lightning arrester and choke coil outfit for 
one 3-phase 4000 volt circuit, (Y connected, neutral grounded at generating plant only, through 
low resistance); also suitable disconnecting switches for the lightning arresters and incoming 
circuit respectively. 

Circuit Breaker. One oil circuit breaker with inverse time limit overload relay and no-voltage 
release, with remote mechanical control. 

Bus Work and Wiring. All bus work and wiring necessary .for connecting the motor to the 
switchboard and to power wires on the outer wall of the pump house, consisting of copper 
conductors, clamps, insulators, pins and pipe frame-work and other details necessary for the 
successful operating of the equipment, are to be furnished and installed by the contractor. 

Power wires o*utside of the pump house are to be installed by the Electric 

Light Co. 

Pump Capacity. The centrifugal pump is to discharge 8,000,000 U. S. gallons in 24 hours from 
a pump well with water at grade 127, through about 2180 feet of new 36" cast iron pipe to a 
standpipe with water at grade 305. There is to be a hydraulically or an electrically operated 
valve and a check valve between the pump and the 36" main. These valves are to be fur- 
nished and installed by the city. 

Head. This 36" pipe will receive an additional 8,000,000 gallons in 24 hours from a second unit 
in the same pumping station or from another station approximately 500 feet away. This 
fact is to be noted in considering the total head the pump is to work against. 

Impeller End Thrust. The pump impeller is to be of bronze or suitable non-corrosive material, 
and unbalanced end thrust on the impeller is to be avoided as far as possible. The pump 



NOTES ON POWER PLANT DESIGN 175 

impeller and the pump casing shall be provided with bronze renewable wearing rings so that 
they may be readily replaced if necessary. 

Impeller Shafts. The impeller shafts are to be protected from corrosion by removable sleeves of 
composition. Composition packing glands and bronze studs are to be provided for the pumps ; 
stuffing boxes on ends of pump shall be provided with water seals. 

Priming Device. The pump is to have a water ejector or other device capable of removing air 
from the pump, in priming, in a period of five minutes. 

Discharge Valve. A hydraulically or electrically operated valve in the discharge pipe of the 
pump and not over 20 feet from the discharge outlet of the pump will be installed by the City 
and all necessary pipmg, valves or wiring and switches needed for the operation of this valve 
are to be furnished and connected up by the contractor. This valve will be closed with the 
pump running at full speed preparatory to shutting down the unit. 

Pump Characteristics. The Contractor must submit with his bid curves showing the char- 
acteristics of the pump he proposes to furnish. He must guarantee also the efficiency of his 
pump at 8,000,000 gallons capacity when working under the total head (previously explained) . 
The pump shall be carefully tested before it leaves the manufacturer's shop to show that the 
efficiency guaranteed has been obtained. A certified test shall be submitted for the approval 

of the Water Board before shipment is made and notice 10 days previous to test 

shall be sent to the Water Board so that it may be present if it desires. 

Should the efficiency of the purnp as determined by the test fall below that guaranteed, 

the Water Board may reject the pump or at its option may accept the pump at 

such reduction in the original contract price as the city of may suffer in monetary 

loss during a period of eight years -through the lower efficiency. 

The Contractor shall furnish the Water Board with the necessary facili- 
ties for carefully inspecting the apparatus during the process of manufacture. 

Foundation. The foundation for the imit will be erected by the city in accordance with draw- 
ings to be furnished by the contractor. The contractor is to supply all foundation bolts 
and plates. The Contractor is to furnish, erect and connect the unit complete up to the 
discharge flange of the pump; also to make necessary and suitable connections for the opera- 
tion of the hydraulically or electrically controlled valve in the discharge pipe. 

AuxiLLVRY Apparatus. The Contractor is to furnish, erect, wire up and make all necessary 
cormections to such auxiliary apparatus as may be required for the quick and successful oper- 
ation of his unit. 

Wrenches. The Contractor is to furnish all special wrenches or tools required in assembling or 
in dismantling either the pump or the motor. 

Gages and Panel. The Contractor to provide a slate panel, dull black finish, matching the 
electrical board and mounted alongside same, containing the following: A seven day clock 
mounted in a brass gage case, black finish; a 10" dial brass mounted suction gage and a 10" 
dial brass mounted delivery gage, — these being connected to the suction and delivery pipes 
respectively. These gages to be marked in feet, pounds, or inches of mercury as may be re- 
quested by the Water Board, and the cases given a black finish. 

Painting. The Contractor is to paint all machinery and piping erected by him. Such castings 
as are in sight from the floor of the pump room are to be made smooth, nicely fitted at all 
joints and flanges, filled with a proper paint filler and painted and striped in such colors as the 
Water Board may direct. 

Debris. The Contractor is to remove all blocking, tools or other material used by him in erect- 
ing and installing his work and to remove all debris of any nature in and around the pumping 
station, produced by him in carrying out this contract, at least 100 feet from station or to 
such place as he may be directed. 

Bids. Bids must be made in duplicate. Each bidder must leave with his bid a properly certi- 
fied check for the sum of two thousand dollars ($2000) payable to the order of the City of 

, which check will be returned to the bidder unless forfeited as hereinafter 

provided. 

Bond. A bond will be required for the faithful performance of the contract in the sum of 50% 
of the contract price with a surety company approved by the mayor. 



176 NOTES ON POWER PLANT DESIGN 

The bidder is requested to name the surety company which will sign this bond in case 
the contract is awarded him. 

If notice of the acceptance of the bid shall, within twenty days after June 20th, 1914, 

be given to the bidder by the Water Board, the bond must be furnished within 

ten days (Sunday excepted) after such notification; and in case of the failure of the bidder 
after such notification to furnish the bond within said time the bid may be considered as aban- 
doned and the certified check accompanying the bid may be forfeited to the City. 

Description. Each bidder is to furnish with his bid detailed description and specifications cover- 
ing the apparatus he purposes to install. 

Drawings. Each bidder is to furnish dimensioned drawings giving the general outside measure- 
ments of the entire apparatus when assembled together with such drawings or cuts as may 
be necessary to show the construction of his apparatus. 

Weights. The individual weights of the rotor, stator and pump are to be given and photographs 
of typical equipment or design proposed should be furnished if possible. 

Wiring. The bidder is to attach to his proposal wiring diagrams and detail drawings of the switch- 
board and power wiring. 

Motor Performance. The bidder is to furnish guarantee as to motor performance when operat- 
ing under the following conditions : 

(1) Speed regulation when operating between no load and full load, stating load at which 
motor is rated. 

(2) Power factor at 25, 50, 75, 100 and 125 per cent load. 

(3) Momentary overload, per cent which motor will carry safely. 

(4) Efficiency based on room temperature of 25° C. at the following percentages of load: 
(Respective ultimate temperatures used in the calculation of each case, to be stated) . 

25, 50, 75, 100 and 125 per cent load. 

(5) Torque: Give pull out and starting torque in terms of full load torque. 

(6) Temperature rise at 125 per cent normal rating for two hours following a run at 
normal rating of sufficient length to enable the motor to attain a constant temperature. 

■ (7) Certified tests covering the preceding to be furnished by the party to whom the con- 
tract is awarded before the apparatus leaves the manufacturer's shop. Shipment not to 

be made until approved by the Water Board. 

Test sheets are to be accompanied by a description of the method of test, which should 
as far as possible be in accordance with the Standardization Rules of the American Institute 

of Electrical Engineers. If doubt arises that the unit has not corne up to test the 

Water Board reserves the right to conduct another test after the installation; the party in error 
being responsible for payment of expenses of test. 

Bearings. The bidder is to guarantee that all bearings will be continuously lubricated and will 
run continuously without overheating. 

Repairs. The bidder is to agree to make all repairs which may be made necessary through original 
faulty construction, design or workmanship, for a period of one year after the unit goes into 
regular service, at his own expense. 

Neither experimental nor unusual types of apparatus will be considered. 

Units Previously Installed. Each bidder must be prepared to prove to the satisfaction of 
the Water Board that he has previously installed units of the type he pro- 
poses to furnish and he shall state where such units are in successful operation. 

The bidder must state the general type, design and builder's name, of any part of the 
unit which is not built at the works of his own company. 

Delivery. The bidder must give the date of delivery and the time required for the erection of 
the completed plant. 

Payments. Payments will be made as follows: One-third of the contract price ten days after 
the delivery of the motor, pump and accessories; one-third within thirty days after satis- 
factory and successful operation; one-third thirty days after the acceptance of the unit by 
the city. 

Acceptance. The '.Water Board reserves the right to reject any or all bids or to 

award the contract as it deems best. 



NOTES ON POWER PLANT DESIGN 177 

The general design and accessibility of the parts, together with the cost will be consid- 
ered in awarding this contract. 
Bidder to Add to his Specifications. The bidder will submit his bid and his specifications 
on his own printed forms and will add to the same the following: 

That he will indemnify and save harmless the city from all claims against the city, mechan- 
ics, laborers, and others for work performed or material furnished for carrying on the contract. 

That he will indemnify and save harmless the city, its agents and employees, from all 
suits and claims against it or them or any of them, for damage to private corporations and 
individuals caused by the construction of the work to be done under this contract; or for the 
use of any invention, patent, or patent right, material, labor or implement by the contractor 
or from any act, omission or neglect by him, his agents, or employees, in carrying on the work; 
and that he agrees that so much of the money due to him under this contract as may be con- 
sidered necessary by the Water Board may be retained by the city until all 

suits or claims for damages as aforesaid shall have been settled and evidence to that effect 
furnished to the Water Board. 

The successful bidder will be required to furnish a certificate to the Water 

Board certifying that the men employed by him on the work herein set forth are insured under 
the provision of the Workmen's Compensation Act, so-called, of Massachusetts. 

That he agrees to do such extra work as may be ordered in writing by the 

Water Board, and to receive in payment for same its reasonable cost as estimated by the 
Water Board plus fifteen per cent of said estimated cost. 

That he agrees to make no claim for compensation for extra work unless the same is 
ordered in writing by the Water Board. 

And that he still further agrees that the Water Board may make altera- 
tions in the work provided that if such changes increase the cost he shall be fairly remunerated 
and in case they diminish the cost, the proper reduction from the contract price shall be made, 
— the amount to be paid or deducted to be determined by the Water Board. 

MASSACHUSETTS INSTITUTE OF TECHNOLOGY 
Coal Supply — 1914-1915 

The Massachusetts Institute of Technology invites your bid on its supply of coal for the forth- 
coming fiscal year, July 1, 1914-July 1, 1915, on the following terms: 

(1) Delivery 

Daily, as called for, at 491 Boylston St., rear of 26 Trinity Place, Garrison St., and else- 
where, if desired, at the Technology buildings. 

(2) Kinds and Amounts 

(a) No. 2 Buckwheat, 2700 tons, more or less 

(b) Semi-bituminous, 3800 tons, more or less 

(3) Specifications 

(a) No. 2 Buckwheat — free from dust. 

(b) Semi-bituminous — of good steaming quality. The coal offered should be specified 
in terms of moisture "as received," ash, volatile matter, sulphur and B. T. U., "dry coal" 
basis, which values become the standards for the coal of the successful bidder. The trade 
name of the coal should be given. 

(4) Prices and Payments 

(a) No. 2 Buckwheat — payments monthly at price named. 

(b) Semi-bituminous — payments monthly on the basis of price named in bid, corrected 
for variations as to heat value, ash and moisture above or below, as follows: 

Heat Value — On a "dry coal" basis, no adjustment in price will be made for variations 
of 1% or less in the number of B. T. U.'s from the guaranteed standard. When such varia- 
tions exceed 1%, the adjustment will be proportional and determined as follows: 

B. T. U. delivered coal, "dry" ^.^ . 

B.T.U. specified in bid "" ^'^ P^^^" = '"^^^^^^S pnce. 



178 NOTES ON POWER PLANT DESIGN 

Ash — On a "dry coal" basis, no adjustment in price will be made for variations of 1% 

or less above or below the per cent of ash guaranteed. When such variation exceeds 1%, the 

adjustment in price will be determined as follows: 

The difference between the ash content of analysis and the ash content guaranteed 
will be divided by 2 and the quotient multiplied by bid price, the result to be added to 
or subsracted from the B. T. U. adjusted price or the bid price, if there is no B. T. U. 
adjustment, according to whether the ash content by analysis is below or above the per- 
centage guaranteed. 
Moisture — The price will be further adjusted for moisture content in excess of amount 

guaranteed, the deduction being determined by multiplying the price bid by the percentage of 

moisture in excess of the amount guaranteed. 

(5) Sampling and Testing 

The samples of coal shall be taken by the Institute or its representative and no other 
sample will be recognized. The coal dealer or his representative may witness the operation 
of the sampling if so deptred. Samples of the coal delivered will be taken by the Institute or 
its representative from the wagons while being unloaded. Two or more shovelfuls of coal 
shall be taken from each wagon load and placed in a metal receptacle under lock. Not less 
than three times in any one month the samples, thus accimiulated, shall be thoroughly mixed 
and quartered in the usual manner. The final sample is to be pulverized and passed through 
an 80-mesh sieve. A part of the final sample shall be put aside in an air-tight jar properly 
marked, for the coal dealer, so that he may verify results if he so desires. 

The coal shall be dried for one hour in dry air at a temperature between 104° C. and 105° C. 

The coal shall be tested by the Institute, a bomb calorimeter being used. Should the 
coal dealer question the results, a sufiicient quantity of the original sample is to be furnished 
him for testing if he so requests it. 

The average of the results of the tests made each month shall be the basis for determining 
the price to be paid for coal delivered during that month. 

(6) Limits 

Should the heating value per pound of dry coal fall below 14,500 B. T. U., or should the 
moisture exceed 3%, or the ash exceed 7%, or the sulphur 1%, or the volatile matter 20%, 
the agreement may be terminated at the option of the Institute. 

(7) The Right to reject any or all bids is reserved by the Institute. 




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SECTIONAL ELEVATION OF PORT MORRIS STATION. 




— eoston Edison L Street Power-House. 




-Lots Road, Chelsea : Sectional Elevation. 




,. — Quincy Point Power- House: Elevatioa 



LbAp'16 



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LIBRARY OF CONGRESS 



021 213 123 4 



